Refrigeration cycle apparatus

ABSTRACT

An air conditioning unit capable of performing a refrigeration cycle using a small-GWP refrigerant is provided. A refrigeration cycle apparatus ( 1, 1   a  to  1   m ) includes a refrigerant circuit ( 10 ) including a compressor ( 21 ), a condenser ( 23, 31, 36 ), a decompressing section ( 24, 44, 45, 33, 38 ), and an evaporator ( 31, 36, 23 ), and a refrigerant containing at least 1,2-difluoroethylene enclosed in the refrigerant circuit ( 10 ).

TECHNICAL FIELD

The present disclosure relates to a refrigeration cycle apparatus.

BACKGROUND ART

Conventionally, heat cycle systems such as air conditioning apparatusesuse in many cases R410A as a refrigerant. R410A is a two-component mixedrefrigerant of difluoromethane (CH₂F2; HFC-32 or R32) andpentafluoroethane (C₂HF₅; HFC-125 or R125), and is a pseudo-azeotropiccomposition.

However, R410A has a global warming potential (GWP) of 2088. In recentyears, R32 which is a refrigerant having a lower GWP is being more usedas a result of growing concern about global warming.

Due to this, for example, PTL 1 (International Publication No.2015/141678) suggests various low-GWP mixed refrigerants alternative toR410A.

SUMMARY OF THE INVENTION Technical Problem

However, a specific refrigerant circuit that can use such a small-GWPrefrigerant has not been studied at all.

The content of the present disclosure aims at the above-described pointand an object of the present disclosure is to provide an airconditioning unit capable of performing a refrigeration cycle using asmall-GWP refrigerant.

Solution to Problem

A refrigeration cycle apparatus according to a first aspect includes arefrigerant circuit and a refrigerant. The refrigerant circuit includesa compressor, a condenser, a decompressing section, and an evaporator.The refrigerant contains at least 1,2-difluoroethylene. The refrigerantis enclosed in the refrigerant circuit.

Since the refrigeration cycle apparatus can perform a refrigerationcycle using the refrigerant containing 1,2-difluoroethylene in therefrigerant circuit including the compressor, the condenser, thedecompressing section, and the evaporator, the refrigeration cycleapparatus can perform a refrigeration cycle using a small-GWPrefrigerant.

A refrigeration cycle apparatus according to a second aspect is therefrigeration cycle apparatus according to the first aspect, in whichthe refrigerant circuit further includes a low-pressure receiver. Thelow-pressure receiver is provided midway in a refrigerant flow pathextending from the evaporator toward a suction side of the compressor.

The refrigeration cycle apparatus can perform a refrigeration cyclewhile the low-pressure receiver stores an excessive refrigerant in therefrigerant circuit.

A refrigeration cycle apparatus according to a third aspect is therefrigeration cycle apparatus according to the first aspect or thesecond aspect, in which the refrigerant circuit further includes ahigh-pressure receiver. The high-pressure receiver is provided midway ina refrigerant flow path extending from the condenser toward theevaporator.

The refrigeration cycle apparatus can perform a refrigeration cyclewhile the high-pressure receiver stores an excessive refrigerant in therefrigerant circuit.

A refrigeration cycle apparatus according to a fourth aspect is therefrigeration cycle apparatus according to any one of the first aspectto the third aspect, in which the refrigerant circuit further includes afirst decompressing section, a second decompressing section, and anintermediate-pressure receiver. The first decompressing section, thesecond decompressing section, and the intermediate-pressure receiver areprovided midway in a refrigerant flow path extending from the condensertoward the evaporator. The intermediate-pressure receiver is providedbetween the first decompressing section and the second decompressingsection in the refrigerant flow path extending from the condenser towardthe evaporator.

The refrigeration cycle apparatus can perform a refrigeration cyclewhile the intermediate-pressure receiver stores an excessive refrigerantin the refrigerant circuit.

A refrigeration cycle apparatus according to a fifth aspect is therefrigeration cycle apparatus according to any one of the first aspectto the fourth aspect, in which the refrigeration cycle apparatus furtherincludes a control unit. The refrigerant circuit further includes afirst decompressing section and a second decompressing section. Thefirst decompressing section and the second decompressing section areprovided midway in a refrigerant flow path extending from the condensertoward the evaporator. The control unit adjusts both a degree ofdecompression of a refrigerant passing through the first decompressingsection and a degree of decompression of a refrigerant passing throughthe second decompressing section.

The refrigeration cycle apparatus, by controlling the respective degreesof decompression of the first decompressing section and the seconddecompressing section provided midway in the refrigerant flow pathextending from the condenser toward the evaporator, can decrease theconcentration of the refrigerant located between the first decompressingsection and the second decompressing section provided midway in therefrigerant flow path extending from the condenser toward theevaporator. Thus, the refrigerant enclosed in the refrigerant circuit islikely present more in the condenser and/or the evaporator, therebyimproving the capacity.

A refrigeration cycle apparatus according to a sixth aspect is therefrigeration cycle apparatus according to any one of the first aspectto the fifth aspect, in which the refrigerant circuit further includes arefrigerant heat exchanging section. The refrigerant heat exchangingsection causes a refrigerant flowing from the condenser toward theevaporator and a refrigerant flowing from the evaporator toward thecompressor to exchange heat with each other.

With the refrigeration cycle apparatus, in the refrigerant heatexchanging section, the refrigerant flowing from the evaporator towardthe compressor is heated with the refrigerant flowing from the condensertoward the evaporator. Thus, liquid compression by the compressor can becontrolled.

A refrigeration cycle apparatus according to a seventh aspect is therefrigeration cycle apparatus according to any of the first throughsixth aspects, wherein the refrigerant comprisestrans-1,2-difluoroethylene (FO-1132(E)), trifluoroethylene (HFO-1123),and 2,3,3,3-tetrafluoro-1-propene (R1234yf).

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, and a refrigeration capacity (possibly referred to as coolingcapacity or capacity) and a coefficient of performance (COP) equivalentto those of R410A.

A refrigeration cycle apparatus according to an eighth aspect is therefrigeration cycle apparatus according to the seventh aspect, whereinwhen the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumin the refrigerant is respectively represented by x, y, and z,coordinates (x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R1234yf is 100 mass % are within the range ofa figure surrounded by line segments AA′, A′B, BD, DC′, C′C, CO, and OAthat connect the following 7 points:

point A (68.6, 0.0, 31.4),

point A′ (30.6, 30.0, 39.4),

point B (0.0, 58.7, 41.3),

point D (0.0, 80.4, 19.6),

point C′ (19.5, 70.5, 10.0),

point C (32.9, 67.1, 0.0), and

point O (100.0, 0.0, 0.0),

or on the above line segments (excluding the points on the line segmentsBD, CO, and OA);

the line segment AA′ is represented by coordinates (x,0.0016x²−0.9473x+57.497, −0.0016x²−0.0527x+42.503),

the line segment A′B is represented by coordinates (x,0.0029x²−1.0268x+58.7, −0.0029x²+0.0268x+41.3),

the line segment DC′ is represented by coordinates (x,0.0082x²−0.6671x+80.4, −0.0082x²−0.3329x+19.6),

the line segment C′C is represented by coordinates (x,0.0067x²−0.6034x+79.729, −0.0067x²−0.3966x+20.271), and

the line segments BD, CO, and OA are straight lines.

A refrigeration cycle apparatus according to a ninth aspect is therefrigeration cycle apparatus according to the seventh aspect, wherein

when the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumin the refrigerant is respectively represented by x, y, and z,coordinates (x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R1234yf is 100 mass % are within the range ofa figure surrounded by line segments GI, IA, AA′, A′B, BD, DC′, C′C, andCG that connect the following 8 points:

point G (72.0, 28.0, 0.0),

point I (72.0, 0.0, 28.0),

point A (68.6, 0.0, 31.4),

point A′ (30.6, 30.0, 39.4),

point B (0.0, 58.7, 41.3),

point D (0.0, 80.4, 19.6),

point C′ (19.5, 70.5, 10.0), and

point C (32.9, 67.1, 0.0),

or on the above line segments (excluding the points on the line segmentsIA, BD, and CG);

the line segment AA′ is represented by coordinates (x,0.0016x²−0.9473x+57.497, −0.0016x²−0.0527x+42.503),

the line segment A′B is represented by coordinates (x,0.0029x²−1.0268x+58.7, −0.0029x²+0.0268x+41.3),

the line segment DC′ is represented by coordinates (x,0.0082x²−0.6671x+80.4, −0.0082x²−0.3329x+19.6),

the line segment C′C is represented by coordinates (x,0.0067x²−0.6034x+79.729, −0.0067x²−0.3966x+20.271), and

the line segments GI, IA, BD, and CG are straight lines.

A refrigeration cycle apparatus according to a tenth aspect is therefrigeration cycle apparatus according to the seventh aspect, wherein

when the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumin the refrigerant is respectively represented by x, y, and z,coordinates (x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R1234yf is 100 mass % are within the range ofa figure surrounded by line segments JP, PN, NK, KA′, A′B, BD, DC′, C′C,and CJ that connect the following 9 points:

point J (47.1, 52.9, 0.0),

point P (55.8, 42.0, 2.2),

point N (68.6, 16.3, 15.1),

point K (61.3, 5.4, 33.3),

point A′ (30.6, 30.0, 39.4),

point B (0.0, 58.7, 41.3),

point D (0.0, 80.4, 19.6),

point C′ (19.5, 70.5, 10.0), and

point C (32.9, 67.1, 0.0),

or on the above line segments (excluding the points on the line segmentsBD and CJ);

the line segment PN is represented by coordinates (x,−0.1135x+12.112x−280.43, 0.1135x²−13.112x+380.43),

the line segment NK is represented by coordinates (x,0.2421x²−29.955x+931.91, −0.2421x²+28.955x−831.91),

the line segment KA′ is represented by coordinates (x,0.0016x²−0.9473x+57.497, −0.0016x²−0.0527x+42.503),

the line segment A′B is represented by coordinates (x,0.0029x²−1.0268x+58.7, −0.0029x²+0.0268x+41.3),

the line segment DC′ is represented by coordinates (x,0.0082x²−0.6671x+80.4, −0.0082x²−0.3329x+19.6),

the line segment C′C is represented by coordinates (x,0.0067x²−0.6034x+79.729, −0.0067x²−0.3966x+20.271), and

the line segments JP, BD, and CG are straight lines.

A refrigeration cycle apparatus according to an eleventh aspect is therefrigeration cycle apparatus according to the seventh aspect, wherein

when the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumin the refrigerant is respectively represented by x, y, and z,coordinates (x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R1234yf is 100 mass % are within the range ofa figure surrounded by line segments JP, PL, LM, MA′, A′B, BD, DC′, C′C,and CJ that connect the following 9 points:

point J (47.1, 52.9, 0.0),

point P (55.8, 42.0, 2.2),

point L (63.1, 31.9, 5.0),

point M (60.3, 6.2, 33.5),

point A′ (30.6, 30.0, 39.4),

point B (0.0, 58.7, 41.3),

point D (0.0, 80.4, 19.6),

point C′ (19.5, 70.5, 10.0), and

point C (32.9, 67.1, 0.0),

or on the above line segments (excluding the points on the line segmentsBD and CJ);

the line segment PL is represented by coordinates (x,−0.1135x²+12.112x−280.43, 0.1135x²−13.112x+380.43) the line segment MA′is represented by coordinates (x, 0.0016x²−0.9473x+57.497,−0.0016x²−0.0527x+42.503),

the line segment A′B is represented by coordinates (x,0.0029x²−1.0268x+58.7, −0.0029x²+0.0268x+41.3),

the line segment DC′ is represented by coordinates (x,0.0082x²−0.6671x+80.4, −0.0082x²−0.3329x+19.6),

the line segment C′C is represented by coordinates (x,0.0067x²−0.6034x+79.729, −0.0067x²−0.3966x+20.271), and

the line segments JP, LM, BD, and CG are straight lines.

A refrigeration cycle apparatus according to a twelfth aspect is therefrigeration cycle apparatus according to the seventh aspect, wherein

when the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumin the refrigerant is respectively represented by x, y, and z,coordinates (x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R1234yf is 100 mass % are within the range ofa figure surrounded by line segments PL, LM, MA′, A′B, BF, FT, and TPthat connect the following 7 points:

point P (55.8, 42.0, 2.2),

point L (63.1, 31.9, 5.0),

point M (60.3, 6.2, 33.5),

point A′ (30.6, 30.0, 39.4),

point B (0.0, 58.7, 41.3),

point F (0.0, 61.8, 38.2), and

point T (35.8, 44.9, 19.3),

or on the above line segments (excluding the points on the line segmentBF);

the line segment PL is represented by coordinates (x,−0.1135x²+12.112x−280.43, 0.1135x²−13.112x+380.43),

the line segment MA′ is represented by coordinates (x,0.0016x²−0.9473x+57.497, −0.0016x²−0.0527x+42.503),

the line segment A′B is represented by coordinates (x,0.0029x²−1.0268x+58.7, −0.0029x²+0.0268x+41.3),

the line segment FT is represented by coordinates (x,0.0078x²−0.7501x+61.8, −0.0078x²−0.2499x+38.2),

the line segment TP is represented by coordinates (x,0.00672x²−0.7607x+63.525, −0.00672x²−0.2393x+36.475), and

the line segments LM and BF are straight lines.

A refrigeration cycle apparatus according to a thirteenth aspect is therefrigeration cycle apparatus according to the seventh aspect, wherein

when the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumin the refrigerant is respectively represented by x, y, and z,coordinates (x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R1234yf is 100 mass % are within the range ofa figure surrounded by line segments PL, LQ, QR, and RP that connect thefollowing 4 points:

point P (55.8, 42.0, 2.2),

point L (63.1, 31.9, 5.0),

point Q (62.8, 29.6, 7.6), and

point R (49.8, 42.3, 7.9),

or on the above line segments;

the line segment PL is represented by coordinates (x,−0.1135x²+12.112x−280.43, 0.1135x²−13.112x+380.43),

the line segment RP is represented by coordinates (x,0.00672x²−0.7607x+63.525, −0.00672x²−0.2393x+36.475), and

the line segments LQ and QR are straight lines.

A refrigeration cycle apparatus according to a fourteenth aspect is therefrigeration cycle apparatus according to the seventh aspect, wherein

when the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumin the refrigerant is respectively represented by x, y, and z,coordinates (x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R1234yf is 100 mass % are within the range ofa figure surrounded by line segments SM, MA′, A′B, BF, FT, and TS thatconnect the following 6 points:

point S (62.6, 28.3, 9.1),

point M (60.3, 6.2, 33.5),

point A′ (30.6, 30.0, 39.4),

point B (0.0, 58.7, 41.3),

point F (0.0, 61.8, 38.2), and

point T (35.8, 44.9, 19.3),

or on the above line segments,

the line segment MA′ is represented by coordinates (x,0.0016x²−0.9473x+57.497, −0.0016x²−0.0527x+42.503),

the line segment A′B is represented by coordinates (x,0.0029x²−1.0268x+58.7, −0.0029x²+0.0268x+41.3),

the line segment FT is represented by coordinates (x,0.0078x²−0.7501x+61.8, −0.0078x²−0.2499x+38.2),

the line segment TS is represented by coordinates (x,−0.0017x²−0.7869x+70.888, −0.0017x²−0.2131x+29.112), and

the line segments SM and BF are straight lines.

A refrigeration cycle apparatus according to a fifteenth aspect is therefrigeration cycle apparatus according to any of the first throughsixth aspects, wherein

the refrigerant comprises trans-1,2-difluoroethylene (HFO-1132(E)) andtrifluoroethylene (HFO-1123) in a total amount of 99.5 mass % or morebased on the entire refrigerant, and the refrigerant comprises 62.0 mass% to 72.0 mass % of HFO-1132(E) based on the entire refrigerant.

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, a coefficient of performance (COP) and a refrigeration capacity(possibly referred to as cooling capacity or capacity) equivalent tothose of R410A, and being classified with lower flammability (class 2L)according to the standard of the American Society of Heating,Refrigerating and Air-Conditioning Engineers (ASHRAE).

A refrigeration cycle apparatus according to a sixteenth aspect is therefrigeration cycle apparatus according to any of the first throughsixth aspects, wherein

the refrigerant comprises HFO-1132(E) and HFO-1123 in a total amount of99.5 mass % or more based on the entire refrigerant, and

the refrigerant comprises 45.1 mass % to 47.1 mass % of HFO-1132(E)based on the entire refrigerant.

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, a coefficient of performance (COP) and a refrigeration capacity(possibly referred to as cooling capacity or capacity) equivalent tothose of R410A, and being classified with lower flammability (class 2L)according to the standard of the American Society of Heating,Refrigerating and Air-Conditioning Engineers (ASHRAE).

A refrigeration cycle apparatus according to a seventeenth aspect is therefrigeration cycle apparatus according to any of the first throughsixth aspects, wherein

the refrigerant comprises trans-1,2-difluoroethylene (HFO-1132(E)),trifluoroethylene (HFO-1123), 2,3,3,3-tetrafluoro-1-propene (R1234yf),and difluoromethane (R32),

wherein

when the mass % of HFO-1132(E), HFO-1123, R1234yf, and R32 based ontheir sum in the refrigerant is respectively represented by x, y, z, anda,

if 0<a≤11.1, coordinates (x,y,z) in a ternary composition diagram inwhich the sum of HFO-1132(E), HFO-1123, and R1234yf is (100−a) mass %are within the range of a figure surrounded by straight lines GI, IA,AB, BD′, D′C, and CG that connect the following 6 points:

point G (0.026a²−1.7478a+72.0, −0.026a²+0.7478a+28.0, 0.0),

point I (0.026a²−1.7478a+72.0, 0.0, −0.026a²+0.7478a+28.0),

point A (0.0134a²−1.9681a+68.6, 0.0, −0.0134a²+0.9681a+31.4),

point B (0.0, 0.0144a²−1.6377a+58.7, −0.0144a²+0.6377a+41.3),

point D′ (0.0, 0.0224a²+0.968a+75.4, −0.0224a²−1.968a+24.6), and

point C (−0.2304a²−0.4062a+32.9, 0.2304a²−0.5938a+67.1, 0.0),

or on the straight lines GI, AB, and D′C (excluding point G, point I,point A, point B, point D′, and point C);

if 11.1<a≤18.2, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines GI, IA,AB, BW, and WG that connect the following 5 points:

point G (0.02a²−1.6013a+71.105, −0.02a²+0.6013a+28.895, 0.0),

point I (0.02a²−1.6013a+71.105, 0.0, −0.02a²+0.6013a+28.895),

point A (0.0112a²−1.9337a+68.484, 0.0, −0.0112a²+0.9337a+31.516),

point B (0.0, 0.0075a²−1.5156a+58.199, −0.0075a²+0.5156a+41.801), and

point W (0.0, 100.0−a, 0.0),

or on the straight lines GI and AB (excluding point G, point I, point A,point B, and point W);

if 18.2<a≤26.7, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines GI, IA,AB, BW, and WG that connect the following 5 points:

point G (0.0135a²−1.4068a+69.727, −0.0135a²+0.4068a+30.273, 0.0),

point I (0.0135a²−1.4068a+69.727, 0.0, −0.0135a²+0.4068a+30.273),

point A (0.0107a²−1.9142a+68.305, 0.0, −0.0107a²+0.9142a+31.695),

point B (0.0, 0.009a²−1.6045a+59.318, −0.009a²+0.6045a+40.682), and

point W (0.0, 100.0−a, 0.0),

or on the straight lines GI and AB (excluding point G, point I, point A,point B, and point W);

if 26.7<a≤36.7, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines GI, IA,AB, BW, and WG that connect the following 5 points:

point G (0.0111a²−1.3152a+68.986, −0.0111a²+0.3152a+31.014, 0.0),

point I (0.0111a²−1.3152a+68.986, 0.0, −0.0111a²+0.3152a+31.014),

point A (0.0103a²−1.9225a+68.793, 0.0, −0.0103a²+0.9225a+31.207),

point B (0.0, 0.0046a²−1.41a+57.286, −0.0046a²+0.41a+42.714), and

point W (0.0, 100.0−a, 0.0),

or on the straight lines GI and AB (excluding point G, point I, point A,point B, and point W); and

if 36.7<a≤46.7, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines GI, IA,AB, BW, and WG that connect the following 5 points:

point G (0.0061a²−0.9918a+63.902, −0.0061a²−0.0082a+36.098, 0.0),

point I (0.0061a²−0.9918a+63.902, 0.0, −0.0061a²−0.0082a+36.098),

point A (0.0085a²−1.8102a+67.1, 0.0, −0.0085a²+0.8102a+32.9),

point B (0.0, 0.0012a²−1.1659a+52.95, −0.0012a²+0.1659a+47.05), and

point W (0.0, 100.0−a, 0.0),

or on the straight lines GI and AB (excluding point G, point I, point A,point B, and point W).

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, and a refrigeration capacity (possibly referred to as coolingcapacity or capacity) and a coefficient of performance (COP) equivalentto those of R410A.

A refrigeration cycle apparatus according to an eighteenth aspect is therefrigeration cycle apparatus according to any of the first throughsixth aspects, wherein

the refrigerant comprises trans-1,2-difluoroethylene (HFO-1132(E)),trifluoroethylene (HFO-1123), 2,3,3,3-tetrafluoro-1-propene (R1234yf),and difluoromethane (R32),

wherein

when the mass % of HFO-1132(E), HFO-1123, R1234yf, and R32 based ontheir sum in the refrigerant is respectively represented by x, y, z, anda,

if 0<a≤11.1, coordinates (x,y,z) in a ternary composition diagram inwhich the sum of HFO-1132(E), HFO-1123, and R1234yf is (100−a) mass %are within the range of a figure surrounded by straight lines JK′, K′B,BD′, D′C, and CJ that connect the following 5 points:

point J (0.0049a²−0.9645a+47.1, −0.0049a²−0.0355a+52.9, 0.0),

point K′ (0.0514a²−2.4353a+61.7, −0.0323a²+0.4122a+5.9,−0.0191a²+1.0231a+32.4),

point B (0.0, 0.0144a²−1.6377a+58.7, −0.0144a²+0.6377a+41.3),

point D′ (0.0, 0.0224a²+0.968a+75.4, −0.0224a²−1.968a+24.6), and

point C (−0.2304a²−0.4062a+32.9, 0.2304a²−0.5938a+67.1, 0.0),

or on the straight lines JK′, K′B, and D′C (excluding point J, point B,point D′, and point C);

if 11.1<a≤18.2, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines JK′, K′B,BW, and WJ that connect the following 4 points:

point J (0.0243a²−1.4161a+49.725, −0.0243a²+0.4161a+50.275, 0.0),

point K′ (0.0341a²−2.1977a+61.187, −0.0236a²+0.34a+5.636,−0.0105a²+0.8577a+33.177),

point B (0.0, 0.0075a²−1.5156a+58.199, −0.0075a²+0.5156a+41.801), and

point W (0.0, 100.0−a, 0.0),

or on the straight lines JK∝ and K′B (excluding point J, point B, andpoint W);

if 18.2<a≤26.7, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines JK′, K′B,BW, and WJ that connect the following 4 points:

point J (0.0246a²−1.4476a+50.184, −0.0246a²+0.4476a+49.816, 0.0),

point K′ (0.0196a²−1.7863a+58.515, −0.0079a²−0.1136a+8.702,−0.0117a²+0.8999a+32.783),

point B (0.0, 0.009a²−1.6045a+59.318, −0.009a²+0.6045a+40.682), and

point W (0.0, 100.0−a, 0.0),

or on the straight lines JK′ and K′B (excluding point J, point B, andpoint W);

if 26.7<a≤36.7, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines JK′, K′A,AB, BW, and WJ that connect the following 5 points:

point J (0.0183a²−1.1399a+46.493, −0.0183a²+0.1399a+53.507, 0.0),

point K′ (−0.0051a²+0.0929a+25.95, 0.0, 0.0051a²−1.0929a+74.05),

point A (0.0103a²−1.9225a+68.793, 0.0, −0.0103a²+0.9225a+31.207),

point B (0.0, 0.0046a²−1.41a+57.286, −0.0046a²+0.41a+42.714), and

point W (0.0, 100.0−a, 0.0),

or on the straight lines JK′, K′A, and AB (excluding point J, point B,and point W); and

if 36.7<a≤46.7, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines JK′, K′A,AB, BW, and WJ that connect the following 5 points:

point J (−0.0134a²+1.0956a+7.13, 0.0134a²−2.0956a+92.87, 0.0),

point K′(−1.892a+29.443, 0.0, 0.892a+70.557),

point A (0.0085a²−1.8102a+67.1, 0.0, −0.0085a²+0.8102a+32.9),

point B (0.0, 0.0012a²−1.1659a+52.95, −0.0012a²+0.1659a+47.05), and

point W (0.0, 100.0−a, 0.0),

or on the straight lines JK′, K′A, and AB (excluding point J, point B,and point W).

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, and a refrigeration capacity (possibly referred to as coolingcapacity or capacity) and a coefficient of performance (COP) equivalentto those of R410A.

A refrigeration cycle apparatus according to a nineteenth aspect is therefrigeration cycle apparatus according to any of the first throughsixth aspects, wherein

the refrigerant comprises trans-1,2-difluoroethylene (HFO-1132(E)),difluoromethane(R32), and 2,3,3,3-tetrafluoro-1-propene (R1234yf),

wherein

when the mass % of HFO-1132(E), R32, and R1234yf based on their sum inthe refrigerant is respectively represented by x, y, and z, coordinates(x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), R32, and R1234yf is 100 mass % are within the range of afigure surrounded by line segments IJ, JN, NE, and EI that connect thefollowing 4 points:

point I (72.0, 0.0, 28.0),

point J (48.5, 18.3, 33.2),

point N (27.7, 18.2, 54.1), and

point E (58.3, 0.0, 41.7),

or on these line segments (excluding the points on the line segment EI;

the line segment IJ is represented by coordinates(0.0236y²−1.7616y+72.0, y, −0.0236y²+0.7616y+28.0);

the line segment NE is represented by coordinates (0.012y²−1.9003y+58.3,y, −0.012y²+0.9003y+41.7); and

the line segments JN and EI are straight lines.

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, a refrigeration capacity (possibly referred to as cooling capacityor capacity) equivalent to that of R410A, and being classified withlower flammability (class 2L) according to the standard of the AmericanSociety of Heating, Refrigerating and Air-Conditioning Engineers(ASHRAE).

A refrigeration cycle apparatus according to a twentieth aspect is therefrigeration cycle apparatus according to any of the first throughsixth aspects, wherein

the refrigerant comprises HFO-1132(E), R32, and R1234yf, wherein

when the mass % of HFO-1132(E), R32, and R1234yf based on their sum inthe refrigerant is respectively represented by x, y, and z, coordinates(x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), R32, and R1234yf is 100 mass % are within the range of afigure surrounded by line segments MM′, M′N, NV, VG, and GM that connectthe following 5 points:

point M (52.6, 0.0, 47.4),

point M′ (39.2, 5.0, 55.8),

point N (27.7, 18.2, 54.1),

point V (11.0, 18.1, 70.9), and

point G (39.6, 0.0, 60.4),

or on these line segments (excluding the points on the line segment GM);

the line segment MM′ is represented by coordinates (0.132y²−3.34y+52.6,y, −0.132y²+2.34y+47.4);

the line segment M′N is represented by coordinates(0.0596y²−2.2541y+48.98, y, −0.0596y²+1.2541y+51.02);

the line segment VG is represented by coordinates(0.0123y²−1.8033y+39.6, y, −0.0123y²+0.8033y+60.4); and

the line segments NV and GM are straight lines.

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, a refrigeration capacity (possibly referred to as cooling capacityor capacity) equivalent to that of R410A, and being classified withlower flammability (class 2L) according to the standard of the AmericanSociety of Heating, Refrigerating and Air-Conditioning Engineers(ASHRAE).

A refrigeration cycle apparatus according to a twenty first aspect isthe refrigeration cycle apparatus according to any of the first throughsixth aspects, wherein

the refrigerant comprises HFO-1132(E), R32, and R1234yf, wherein

when the mass % of HFO-1132(E), R32, and R1234yf based on their sum inthe refrigerant is respectively represented by x, y and z, coordinates(x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), R32, and R1234yf is 100 mass % are within the range of afigure surrounded by line segments ON, NU, and UO that connect thefollowing 3 points:

point O (22.6, 36.8, 40.6),

point N (27.7, 18.2, 54.1), and

point U (3.9, 36.7, 59.4),

or on these line segments;

the line segment ON is represented by coordinates(0.0072y²−0.6701y+37.512, y, −0.0072y²−0.3299y+62.488);

the line segment NU is represented by coordinates(0.0083y²−1.7403y+56.635, y, −0.0083y²+0.7403y+43.365); and

the line segment UO is a straight line.

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, a refrigeration capacity (possibly referred to as cooling capacityor capacity) equivalent to that of R410A, and being classified withlower flammability (class 2L) according to the standard of the AmericanSociety of Heating, Refrigerating and Air-Conditioning Engineers(ASHRAE).

A refrigeration cycle apparatus according to a twenty second aspect isthe refrigeration cycle apparatus according to any of the first throughsixth aspects, wherein

the refrigerant comprises HFO-1132(E), R32, and R1234yf, wherein

when the mass % of HFO-1132(E), R32, and R1234yf based on their sum inthe refrigerant is respectively represented by x, y, and z, coordinates(x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), R32, and R1234yf is 100 mass % are within the range of afigure surrounded by line segments QR, RT, TL, LK, and KQ that connectthe following 5 points:

point Q (44.6, 23.0, 32.4),

point R (25.5, 36.8, 37.7),

point T (8.6, 51.6, 39.8),

point L (28.9, 51.7, 19.4), and

point K (35.6, 36.8, 27.6),

or on these line segments;

the line segment QR is represented by coordinates(0.0099y²−1.975y+84.765, y, −0.0099y²+0.975y+15.235);

the line segment RT is represented by coordinates(0.0082y²−1.8683y+83.126, y, −0.0082y²+0.8683y+16.874);

the line segment LK is represented by coordinates(0.0049y²−0.8842y+61.488, y, −0.0049y²−0.1158y+38.512);

the line segment KQ is represented by coordinates(0.0095y²−1.2222y+67.676, y, −0.0095y²+0.2222y+32.324); and

the line segment TL is a straight line.

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, a refrigeration capacity (possibly referred to as cooling capacityor capacity) equivalent to that of R410A, and being classified withlower flammability (class 2L) according to the standard of the AmericanSociety of Heating, Refrigerating and Air-Conditioning Engineers(ASHRAE).

A refrigeration cycle apparatus according to a twenty third aspect isthe refrigeration cycle apparatus according to any of the first throughsixth aspects, wherein

the refrigerant comprises HFO-1132(E), R32, and R1234yf, wherein

when the mass % of HFO-1132(E), R32, and R1234yf based on their sum inthe refrigerant is respectively represented by x, y, and z, coordinates(x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), R32, and R1234yf is 100 mass % are within the range of afigure surrounded by line segments PS, ST, and TP that connect thefollowing 3 points:

point P (20.5, 51.7, 27.8),

point S (21.9, 39.7, 38.4), and

point T (8.6, 51.6, 39.8),

or on these line segments;

the line segment PS is represented by coordinates(0.0064y²−0.7103y+40.1, y, −0.0064y²−0.2897y+59.9);

the line segment ST is represented by coordinates(0.0082y²−1.8683y+83.126, y, −0.0082y²+0.8683y+16.874); and

the line segment TP is a straight line.

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, a refrigeration capacity (possibly referred to as cooling capacityor capacity) equivalent to that of R410A, and being classified withlower flammability (class 2L) according to the standard of the AmericanSociety of Heating, Refrigerating and Air-Conditioning Engineers(ASHRAE).

A refrigeration cycle apparatus according to a twenty fourth aspect isthe refrigeration cycle apparatus according to any of the first throughsixth aspects, wherein

the refrigerant comprises trans-1,2-difluoroethylene (HFO-1132(E)),trifluoroethylene (HFO-1123), and difluoromethane (R32),

wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum inthe refrigerant is respectively represented by x, y, and z, coordinates(x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R32 is 100 mass % are within the range of afigure surrounded by line segments IK, KB′, B′H, HR, RG, and GI thatconnect the following 6 points:

point I (72.0, 28.0, 0.0),

point K (48.4, 33.2, 18.4),

point B′ (0.0, 81.6, 18.4),

point H (0.0, 84.2, 15.8),

point R (23.1, 67.4, 9.5), and

point G (38.5, 61.5, 0.0),

or on these line segments (excluding the points on the line segments B′Hand GI);

the line segment IK is represented by coordinates(0.025z²−1.7429z+72.00, −0.025z²+0.7429z+28.0, z),

the line segment HR is represented by coordinates(−0.3123z²+4.234z+11.06, 0.3123z²−5.234z+88.94, z),

the line segment RG is represented by coordinates(−0.0491z²−1.1544z+38.5, 0.0491z²+0.1544z+61.5, z), and

the line segments KB′ and GI are straight lines.

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, and a coefficient of performance (COP) equivalent to that of R410A.

A refrigeration cycle apparatus according to a twenty fifth aspect isthe refrigeration cycle apparatus according to any of the first throughsixth aspects, wherein

the refrigerant comprises HFO-1132(E), HFO-1123, and R32, wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum inthe refrigerant is respectively represented by x, y, and z, coordinates(x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R32 is 100 mass % are within the range of afigure surrounded by line segments IJ, JR, RG, and GI that connect thefollowing 4 points:

point I (72.0, 28.0, 0.0),

point J (57.7, 32.8, 9.5),

point R (23.1, 67.4, 9.5), and

point G (38.5, 61.5, 0.0),

or on these line segments (excluding the points on the line segment GI);

the line segment IJ is represented by coordinates (0.025z²−1.7429z+72.0,−0.025z²+0.7429z+28.0, z),

the line segment RG is represented by coordinates(−0.0491z²−1.1544z+38.5, 0.0491z²+0.1544z+61.5, z), and

the line segments JR and GI are straight lines.

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, and a coefficient of performance (COP) equivalent to that of R410A.

A refrigeration cycle apparatus according to a twenty sixth aspect isthe refrigeration cycle apparatus according to any of the first throughsixth aspects, wherein

the refrigerant comprises HFO-1132(E), HFO-1123, and R32, wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum inthe refrigerant is respectively represented by x, y, and z, coordinates(x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R32 is 100 mass % are within the range of afigure surrounded by line segments MP, PB′, B′H, HR, RG, and GM thatconnect the following 6 points:

point M (47.1, 52.9, 0.0),

point P (31.8, 49.8, 18.4),

point B′ (0.0, 81.6, 18.4),

point H (0.0, 84.2, 15.8),

point R (23.1, 67.4, 9.5), and

point G (38.5, 61.5, 0.0),

or on these line segments (excluding the points on the line segments B′Hand GM);

the line segment MP is represented by coordinates (0.0083z²−0.984z+47.1,−0.0083z²−0.016z+52.9, z),

the line segment HR is represented by coordinates(−0.3123z²+4.234z+11.06, 0.3123z²−5.234z+88.94, z),

the line segment RG is represented by coordinates(−0.0491z²−1.1544z+38.5, 0.0491z²+0.1544z+61.5, z), and

the line segments PB′ and GM are straight lines.

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, and a coefficient of performance (COP) equivalent to that of R410A.

A refrigeration cycle apparatus according to a twenty seventh aspect isthe refrigeration cycle apparatus according to any of the first throughsixth aspects, wherein

the refrigerant comprises HFO-1132(E), HFO-1123, and R32, wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum inthe refrigerant is respectively represented by x, y, and z, coordinates(x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R32 is 100 mass % are within the range of afigure surrounded by line segments MN, NR, RG, and GM that connect thefollowing 4 points:

point M (47.1, 52.9, 0.0),

point N (38.5, 52.1, 9.5),

point R (23.1, 67.4, 9.5), and

point G (38.5, 61.5, 0.0),

or on these line segments (excluding the points on the line segment GM);

the line segment MN is represented by coordinates (0.0083z²−0.984z+47.1,−0.0083z²−0.016z+52.9, z),

the line segment RG is represented by coordinates(−0.0491z²−1.1544z+38.5, 0.0491z²+0.1544z+61.5, z), and

the line segments JR and GI are straight lines.

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, and a coefficient of performance (COP) equivalent to that of R410A.

A refrigeration cycle apparatus according to a twenty eighth aspect isthe refrigeration cycle apparatus according to any of the first throughsixth aspects, wherein

the refrigerant comprises HFO-1132(E), HFO-1123, and R32, wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum inthe refrigerant is respectively represented by x, y, and z, coordinates(x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R32 is 100 mass % are within the range of afigure surrounded by line segments PS, ST, and TP that connect thefollowing 3 points:

point P (31.8, 49.8, 18.4),

point S (25.4, 56.2, 18.4), and

point T (34.8, 51.0, 14.2),

or on these line segments;

the line segment ST is represented by coordinates(−0.0982z²+0.9622z+40.931, 0.0982z²−1.9622z+59.069, z),

the line segment TP is represented by coordinates (0.0083z²−0.984z+47.1,−0.0083z²−0.016z+52.9, z), and

the line segment PS is a straight line.

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, and a coefficient of performance (COP) equivalent to that of R410A.

A refrigeration cycle apparatus according to a twenty ninth aspect isthe refrigeration cycle apparatus according to any of the first throughsixth aspects, wherein

the refrigerant comprises HFO-1132(E), HFO-1123, and R32, wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum inthe refrigerant is respectively represented by x, y, and z, coordinates(x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R32 is 100 mass % are within the range of afigure surrounded by line segments QB″, B″D, DU, and UQ that connect thefollowing 4 points:

point Q (28.6, 34.4, 37.0),

point B″ (0.0, 63.0, 37.0),

point D (0.0, 67.0, 33.0), and

point U (28.7, 41.2, 30.1),

or on these line segments (excluding the points on the line segmentB″D);

the line segment DU is represented by coordinates(−3.4962z²+210.71z−3146.1, 3.4962z²−211.71z+3246.1, z),

the line segment UQ is represented by coordinates(0.0135z²−0.9181z+44.133, −0.0135z²−0.0819z+55.867, z), and

the line segments QB″ and B″D are straight lines.

The refrigeration cycle apparatus can perform a refrigeration cycleusing a refrigerant having properties including a sufficiently smallGWP, and a coefficient of performance (COP) equivalent to that of R410A.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic view of an instrument used for a flammabilitytest.

FIG. 2 is a diagram showing points A to T and line segments that connectthese points in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R1234yf is 100 mass %.

FIG. 3 is a diagram showing points A to C, D′, G, I, J, and K′, and linesegments that connect these points to each other in a ternarycomposition diagram in which the sum of HFO-1132(E), HFO-1123, andR1234yf is (100−a) mass %.

FIG. 4 is a diagram showing points A to C, D′, G, I, J, and K′, and linesegments that connect these points to each other in a ternarycomposition diagram in which the sum of HFO-1132(E), HFO-1123, andR1234yf is 92.9 mass % (the content of R32 is 7.1 mass %).

FIG. 5 is a diagram showing points A to C, D′, G, I, J, K′, and W, andline segments that connect these points to each other in a ternarycomposition diagram in which the sum of HFO-1132(E), HFO-1123, andR1234yf is 88.9 mass % (the content of R32 is 11.1 mass %).

FIG. 6 is a diagram showing points A, B, G, I, J, K′, and W, and linesegments that connect these points to each other in a ternarycomposition diagram in which the sum of HFO-1132(E), HFO-1123, andR1234yf is 85.5 mass % (the content of R32 is 14.5 mass %).

FIG. 7 is a diagram showing points A, B, G, I, J, K′, and W, and linesegments that connect these points to each other in a ternarycomposition diagram in which the sum of HFO-1132(E), HFO-1123, andR1234yf is 81.8 mass % (the content of R32 is 18.2 mass %).

FIG. 8 is a diagram showing points A, B, G, I, J, K′, and W, and linesegments that connect these points to each other in a ternarycomposition diagram in which the sum of HFO-1132(E), HFO-1123, andR1234yf is 78.1 mass % (the content of R32 is 21.9 mass %).

FIG. 9 is a diagram showing points A, B, G, I, J, K′, and W, and linesegments that connect these points to each other in a ternarycomposition diagram in which the sum of HFO-1132(E), HFO-1123, andR1234yf is 73.3 mass % (the content of R32 is 26.7 mass %).

FIG. 10 is a diagram showing points A, B, G, I, J, K′, and W, and linesegments that connect these points to each other in a ternarycomposition diagram in which the sum of HFO-1132(E), HFO-1123, andR1234yf is 70.7 mass % (the content of R32 is 29.3 mass %).

FIG. 11 is a diagram showing points A, B, G, I, J, K′, and W, and linesegments that connect these points to each other in a ternarycomposition diagram in which the sum of HFO-1132(E), HFO-1123, andR1234yf is 63.3 mass % (the content of R32 is 36.7 mass %).

FIG. 12 is a diagram showing points A, B, G, I, J, K′, and W, and linesegments that connect these points to each other in a ternarycomposition diagram in which the sum of HFO-1132(E), HFO-1123, andR1234yf is 55.9 mass % (the content of R32 is 44.1 mass %).

FIG. 13 is a diagram showing points A, B, G, I, J, K′, and W, and linesegments that connect these points to each other in a ternarycomposition diagram in which the sum of HFO-1132(E), HFO-1123, andR1234yf is 52.2 mass % (the content of R32 is 47.8 mass %).

FIG. 14 is a view showing points A to C, E, G, and I to W; and linesegments that connect points A to C, E, G, and I to W in a ternarycomposition diagram in which the sum of HFO-1132(E), R32, and R1234yf is100 mass %.

FIG. 15 is a view showing points A to U; and line segments that connectthe points in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R32 is 100 mass %.

FIG. 16 is a schematic configuration diagram of a refrigerant circuitaccording to a first embodiment.

FIG. 17 is a schematic control block configuration diagram of arefrigeration cycle apparatus according to the first embodiment.

FIG. 18 is a schematic configuration diagram of a refrigerant circuitaccording to a second embodiment.

FIG. 19 is a schematic control block configuration diagram of arefrigeration cycle apparatus according to the second embodiment.

FIG. 20 is a schematic configuration diagram of a refrigerant circuitaccording to a third embodiment.

FIG. 21 is a schematic control block configuration diagram of arefrigeration cycle apparatus according to the third embodiment.

FIG. 22 is a schematic configuration diagram of a refrigerant circuitaccording to a fourth embodiment.

FIG. 23 is a schematic control block configuration diagram of arefrigeration cycle apparatus according to the fourth embodiment.

FIG. 24 is a schematic configuration diagram of a refrigerant circuitaccording to a fifth embodiment.

FIG. 25 is a schematic control block configuration diagram of arefrigeration cycle apparatus according to the fifth embodiment.

FIG. 26 is a schematic configuration diagram of a refrigerant circuitaccording to a sixth embodiment.

FIG. 27 is a schematic control block configuration diagram of arefrigeration cycle apparatus according to the sixth embodiment.

FIG. 28 is a schematic configuration diagram of a refrigerant circuitaccording to a seventh embodiment.

FIG. 29 is a schematic control block configuration diagram of arefrigeration cycle apparatus according to the seventh embodiment.

FIG. 30 is a schematic configuration diagram of a refrigerant circuitaccording to an eighth embodiment.

FIG. 31 is a schematic control block configuration diagram of arefrigeration cycle apparatus according to the eighth embodiment.

FIG. 32 is a schematic configuration diagram of a refrigerant circuitaccording to a ninth embodiment.

FIG. 33 is a schematic control block configuration diagram of arefrigeration cycle apparatus according to the ninth embodiment.

FIG. 34 is a schematic configuration diagram of a refrigerant circuitaccording to a tenth embodiment.

FIG. 35 is a schematic control block configuration diagram of arefrigeration cycle apparatus according to the tenth embodiment.

FIG. 36 is a schematic configuration diagram of a refrigerant circuitaccording to an eleventh embodiment.

FIG. 37 is a schematic control block configuration diagram of arefrigeration cycle apparatus according to the eleventh embodiment.

FIG. 38 is a schematic configuration diagram of a refrigerant circuitaccording to a twelfth embodiment.

FIG. 39 is a schematic control block configuration diagram of arefrigeration cycle apparatus according to the twelfth embodiment.

DESCRIPTION OF EMBODIMENTS (1) Definition of Terms

In the present specification, the term “refrigerant” includes at leastcompounds that are specified in ISO 817 (International Organization forStandardization), and that are given a refrigerant number (ASHRAEnumber) representing the type of refrigerant with “R” at the beginning;and further includes refrigerants that have properties equivalent tothose of such refrigerants, even though a refrigerant number is not yetgiven. Refrigerants are broadly divided into fluorocarbon compounds andnon-fluorocarbon compounds in terms of the structure of the compounds.Fluorocarbon compounds include chlorofluorocarbons (CFC),hydrochlorofluorocarbons (HCFC), and hydrofluorocarbons (HFC).Non-fluorocarbon compounds include propane (R290), propylene (R1270),butane (R600), isobutane (R600a), carbon dioxide (R744), ammonia (R717),and the like.

In the present specification, the phrase “composition comprising arefrigerant” at least includes (1) a refrigerant itself (including amixture of refrigerants), (2) a composition that further comprises othercomponents and that can be mixed with at least a refrigeration oil toobtain a working fluid for a refrigerating machine, and (3) a workingfluid for a refrigerating machine containing a refrigeration oil. In thepresent specification, of these three embodiments, the composition (2)is referred to as a “refrigerant composition” so as to distinguish itfrom a refrigerant itself (including a mixture of refrigerants).Further, the working fluid for a refrigerating machine (3) is referredto as a “refrigeration oil-containing working fluid” so as todistinguish it from the “refrigerant composition.”

In the present specification, when the term “alternative” is used in acontext in which the first refrigerant is replaced with the secondrefrigerant, the first type of “alternative” means that equipmentdesigned for operation using the first refrigerant can be operated usingthe second refrigerant under optimum conditions, optionally with changesof only a few parts (at least one of the following: refrigeration oil,gasket, packing, expansion valve, dryer, and other parts) and equipmentadjustment. In other words, this type of alternative means that the sameequipment is operated with an alternative refrigerant. Embodiments ofthis type of “alternative” include “drop-in alternative,” “nearlydrop-in alternative,” and “retrofit,” in the order in which the extentof changes and adjustment necessary for replacing the first refrigerantwith the second refrigerant is smaller.

The term “alternative” also includes a second type of “alternative,”which means that equipment designed for operation using the secondrefrigerant is operated for the same use as the existing use with thefirst refrigerant by using the second refrigerant. This type ofalternative means that the same use is achieved with an alternativerefrigerant.

In the present specification, the term “refrigerating machine” refers tomachines in general that draw heat from an object or space to make itstemperature lower than the temperature of ambient air, and maintain alow temperature. In other words, refrigerating machines refer toconversion machines that gain energy from the outside to do work, andthat perform energy conversion, in order to transfer heat from where thetemperature is lower to where the temperature is higher.

In the present specification, a refrigerant having a “WCF lowerflammability” means that the most flammable composition (worst case offormulation for flammability: WCF) has a burning velocity of 10 cm/s orless according to the US ANSI/ASHRAE Standard 34-2013. Further, in thepresent specification, a refrigerant having “ASHRAE lower flammability”means that the burning velocity of WCF is 10 cm/s or less, that the mostflammable fraction composition (worst case of fractionation forflammability: WCFF), which is specified by performing a leakage testduring storage, shipping, or use based on ANSI/ASHRAE 34-2013 using WCF,has a burning velocity of 10 cm/s or less, and that flammabilityclassification according to the US ANSI/ASHRAE Standard 34-2013 isdetermined to classified as be “Class 2L.”

In the present specification, a refrigerant having an “RCL of x % ormore” means that the refrigerant has a refrigerant concentration limit(RCL), calculated in accordance with the US ANSI/ASHRAE Standard34-2013, of x % or more. RCL refers to a concentration limit in the airin consideration of safety factors. RCL is an index for reducing therisk of acute toxicity, suffocation, and flammability in a closed spacewhere humans are present. RCL is determined in accordance with theASHRAE Standard. More specifically, RCL is the lowest concentrationamong the acute toxicity exposure limit (ATEL), the oxygen deprivationlimit (ODL), and the flammable concentration limit (FCL), which arerespectively calculated in accordance with sections 7.1.1, 7.1.2, and7.1.3 of the ASHRAE Standard.

In the present specification, temperature glide refers to an absolutevalue of the difference between the initial temperature and the endtemperature in the phase change process of a composition containing therefrigerant of the present disclosure in the heat exchanger of arefrigerant system.

(2) Refrigerant

(2-1) Refrigerant Component

Any one of various refrigerants such as refrigerant A, refrigerant B,refrigerant C, refrigerant D, and refrigerant E, details of theserefrigerant are to be mentioned later, can be used as the refrigerant.

(2-2) Use of Refrigerant

The refrigerant according to the present disclosure can be preferablyused as a working fluid in a refrigerating machine.

The composition according to the present disclosure is suitable for useas an alternative refrigerant for HFC refrigerant such as R410A, R407Cand R404 etc, or HCFC refrigerant such as R22 etc.

(3) Refrigerant Composition

The refrigerant composition according to the present disclosurecomprises at least the refrigerant according to the present disclosure,and can be used for the same use as the refrigerant according to thepresent disclosure. Moreover, the refrigerant composition according tothe present disclosure can be further mixed with at least arefrigeration oil to thereby obtain a working fluid for a refrigeratingmachine.

The refrigerant composition according to the present disclosure furthercomprises at least one other component in addition to the refrigerantaccording to the present disclosure. The refrigerant compositionaccording to the present disclosure may comprise at least one of thefollowing other components, if necessary. As described above, when therefrigerant composition according to the present disclosure is used as aworking fluid in a refrigerating machine, it is generally used as amixture with at least a refrigeration oil. Therefore, it is preferablethat the refrigerant composition according to the present disclosuredoes not substantially comprise a refrigeration oil. Specifically, inthe refrigerant composition according to the present disclosure, thecontent of the refrigeration oil based on the entire refrigerantcomposition is preferably 0 to 1 mass %, and more preferably 0 to 0.1mass %.

(3-1) Water

The refrigerant composition according to the present disclosure maycontain a small amount of water. The water content of the refrigerantcomposition is preferably 0.1 mass % or less based on the entirerefrigerant. A small amount of water contained in the refrigerantcomposition stabilizes double bonds in the molecules of unsaturatedfluorocarbon compounds that can be present in the refrigerant, and makesit less likely that the unsaturated fluorocarbon compounds will beoxidized, thus increasing the stability of the refrigerant composition.

(3-2) Tracer

A tracer is added to the refrigerant composition according to thepresent disclosure at a detectable concentration such that when therefrigerant composition has been diluted, contaminated, or undergoneother changes, the tracer can trace the changes.

The refrigerant composition according to the present disclosure maycomprise a single tracer, or two or more tracers.

The tracer is not limited, and can be suitably selected from commonlyused tracers. Preferably, a compound that cannot be an impurityinevitably mixed in the refrigerant of the present disclosure isselected as the tracer.

Examples of tracers include hydrofluorocarbons,hydrochlorofluorocarbons, chlorofluorocarbons, hydrochlorocarbons,fluorocarbons, deuterated hydrocarbons, deuterated hydrofluorocarbons,perfluorocarbons, fluoroethers, brominated compounds, iodinatedcompounds, alcohols, aldehydes, ketones, and nitrous oxide (N₂O). Thetracer is particularly preferably a hydrofluorocarbon, ahydrochlorofluorocarbon, a chlorofluorocarbon, a fluorocarbon, ahydrochlorocarbon, a fluorocarbon, or a fluoroether.

The following compounds are preferable as the tracer.

FC-14 (tetrafluoromethane, CF₄)

HCC-40 (chloromethane, CH₃Cl)

HFC-23 (trifluoromethane, CHF₃)

HFC-41 (fluoromethane, CH₃Cl)

HFC-125 (pentafluoroethane, CF₃CHF₂)

HFC-134a (1,1,1,2-tetrafluoroethane, CF₃CH₂F)

HFVC-134 (1,1,2,2-tetrafluoroethane, CHF₂CHF₂)

HFC-143a (1,1,1-trifluoroethane, CF₃CH₃)

HFC-143 (1,1,2-trifluoroethane, CHF₂CH₂F)

HFC-152a (1,1-difluoroethane, CHF₂CH₃)

HFVC-152 (1,2-difluoroethane, CH₂FCH₂F)

HFC-161 (fluoroethane, CH₃CH₂F)

HFC-245fa (1,1,1,3,3-pentafluoropropane, CF₃CH₂CHF₂)

HFC-236fa (1,1,1,3,3,3-hexafluoropropane, CF₃CH₂CF₃)

HFC-236ea (1,1,1,2,3,3-hexafluoropropane, CF₃CHFCHF₂)

HFC-227ea (1,1,1,2,3,3,3-heptafluoropropane, CF₃CHFCF₃)

HCFC-22 (chlorodifluoromethane, CHClF₂)

HCFC-31 (chlorofluoromethane, CH₂ClF)

CFC-1113 (chlorotrifluoroethylene, CF₂═CClF)

HFE-125 (trifluoromethyl-difluoromethyl ether, CF₃OCHF₂)

HFE-134a (trifluoromethyl-fluoromethyl ether, CF₃OCH₂F)

HFE-143a (trifluoromethyl-methyl ether, CF₃OCH₃)

HFE-227ea (trifluoromethyl-tetrafluoroethyl ether, CF₃OCHFCF₃)

HFE-236fa (trifluoromethyl-trifluoroethyl ether, CF₃OCH₂CF₃)

The tracer compound may be present in the refrigerant composition at atotal concentration of about 10 parts per million (ppm) to about 1000ppm. Preferably, the tracer compound is present in the refrigerantcomposition at a total concentration of about 30 ppm to about 500 ppm,and most preferably, the tracer compound is present at a totalconcentration of about 50 ppm to about 300 ppm.

(3-3) Ultraviolet Fluorescent Dye

The refrigerant composition according to the present disclosure maycomprise a single ultraviolet fluorescent dye, or two or moreultraviolet fluorescent dyes.

The ultraviolet fluorescent dye is not limited, and can be suitablyselected from commonly used ultraviolet fluorescent dyes.

Examples of ultraviolet fluorescent dyes include naphthalimide,coumarin, anthracene, phenanthrene, xanthene, thioxanthene,naphthoxanthene, fluorescein, and derivatives thereof. The ultravioletfluorescent dye is particularly preferably either naphthalimide orcoumarin, or both.

(3-4) Stabilizer

The refrigerant composition according to the present disclosure maycomprise a single stabilizer, or two or more stabilizers.

The stabilizer is not limited, and can be suitably selected fromcommonly used stabilizers.

Examples of stabilizers include nitro compounds, ethers, and amines.

Examples of nitro compounds include aliphatic nitro compounds, such asnitromethane and nitroethane; and aromatic nitro compounds, such asnitro benzene and nitro styrene.

Examples of ethers include 1,4-dioxane.

Examples of amines include 2,2,3,3,3-pentafluoropropylamine anddiphenylamine.

Examples of stabilizers also include butylhydroxyxylene andbenzotriazole.

The content of the stabilizer is not limited. Generally, the content ofthe stabilizer is preferably 0.01 to 5 mass %, and more preferably 0.05to 2 mass %, based on the entire refrigerant.

(3-5) Polymerization Inhibitor

The refrigerant composition according to the present disclosure maycomprise a single polymerization inhibitor, or two or morepolymerization inhibitors.

The polymerization inhibitor is not limited, and can be suitablyselected from commonly used polymerization inhibitors.

Examples of polymerization inhibitors include 4-methoxy-1-naphthol,hydroquinone, hydroquinone methyl ether, dimethyl-t-butylphenol,2,6-di-tert-butyl-p-cresol, and benzotriazole.

The content of the polymerization inhibitor is not limited. Generally,the content of the polymerization inhibitor is preferably 0.01 to 5 mass%, and more preferably 0.05 to 2 mass %, based on the entirerefrigerant.

(4) Refrigeration Oil-Containing Working Fluid

The refrigeration oil-containing working fluid according to the presentdisclosure comprises at least the refrigerant or refrigerant compositionaccording to the present disclosure and a refrigeration oil, for use asa working fluid in a refrigerating machine. Specifically, therefrigeration oil-containing working fluid according to the presentdisclosure is obtained by mixing a refrigeration oil used in acompressor of a refrigerating machine with the refrigerant or therefrigerant composition. The refrigeration oil-containing working fluidgenerally comprises 10 to 50 mass % of refrigeration oil.

(4-1) Refrigeration Oil

The refrigeration oil is not limited, and can be suitably selected fromcommonly used refrigeration oils. In this case, refrigeration oils thatare superior in the action of increasing the miscibility with themixture and the stability of the mixture, for example, are suitablyselected as necessary.

The base oil of the refrigeration oil is preferably, for example, atleast one member selected from the group consisting of polyalkyleneglycols (PAG), polyol esters (POE), and polyvinyl ethers (PVE).

The refrigeration oil may further contain additives in addition to thebase oil.

The additive may be at least one member selected from the groupconsisting of antioxidants, extreme-pressure agents, acid scavengers,oxygen scavengers, copper deactivators, rust inhibitors, oil agents, andantifoaming agents.

A refrigeration oil with a kinematic viscosity of 5 to 400 cSt at 40° C.is preferable from the standpoint of lubrication.

The refrigeration oil-containing working fluid according to the presentdisclosure may further optionally contain at least one additive.Examples of additives include compatibilizing agents described below.

(4-2) Compatibilizing Agent

The refrigeration oil-containing working fluid according to the presentdisclosure may comprise a single compatibilizing agent, or two or morecompatibilizing agents.

The compatibilizing agent is not limited, and can be suitably selectedfrom commonly used compatibilizing agents.

Examples of compatibilizing agents include polyoxyalkylene glycolethers, amides, nitriles, ketones, chlorocarbons, esters, lactones, arylethers, fluoroethers, and 1,1,1-trifluoroalkanes. The compatibilizingagent is particularly preferably a polyoxyalkylene glycol ether.

(5) Various Refrigerants

Hereinafter, the refrigerants A to E, which are the refrigerants used inthe present embodiment, will be described in detail.

In addition, each description of the following refrigerant A,refrigerant B, refrigerant C, refrigerant D, and refrigerant E is eachindependent. The alphabet which shows a point or a line segment, thenumber of an Examples, and the number of a comparative examples are allindependent of each other among the refrigerant A, the refrigerant B,the refrigerant C, the refrigerant D, and the refrigerant E. Forexample, the first embodiment of the refrigerant A and the firstembodiment of the refrigerant B are different embodiment from eachother.

(5-1) Refrigerant A The refrigerant A according to the presentdisclosure is a mixed refrigerant comprising trans-1,2-difluoroethylene(HFO-1132(E)), trifluoroethylene (HFO-1123), and2,3,3,3-tetrafluoro-1-propene (R1234yf).

The refrigerant A according to the present disclosure has variousproperties that are desirable as an R410A-alternative refrigerant, i.e.,a refrigerating capacity and a coefficient of performance that areequivalent to those of R410A, and a sufficiently low GWP.

The refrigerant A according to the present disclosure is a compositioncomprising HFO-1132(E) and R1234yf, and optionally further comprisingHFO-1123, and may further satisfy the following requirements. Thisrefrigerant also has various properties desirable as an alternativerefrigerant for R410A; i.e., it has a refrigerating capacity and acoefficient of performance that are equivalent to those of R410A, and asufficiently low GWP.

Requirements

Preferable refrigerant A is as follows:

When the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumin the refrigerant is respectively represented by x, y, and z,coordinates (x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R1234yf is 100 mass % are within the range ofa figure surrounded by line segments AA′, A′B, BD, DC′, C′C, CO, and OAthat connect the following 7 points:

point A (68.6, 0.0, 31.4),

point A′ (30.6, 30.0, 39.4),

point B (0.0, 58.7, 41.3),

point D (0.0, 80.4, 19.6),

point C′ (19.5, 70.5, 10.0),

point C (32.9, 67.1, 0.0), and

point O (100.0, 0.0, 0.0),

or on the above line segments (excluding the points on the line CO);

the line segment AA′ is represented by coordinates (x,0.0016x²−0.9473x+57.497, −0.0016x²−0.0527x+42.503),

the line segment A′B is represented by coordinates (x,0.0029x²−1.0268x+58.7, −0.0029x²+0.0268x+41.3,

the line segment DC′ is represented by coordinates (x,0.0082x²−0.6671x+80.4, −0.0082x²−0.3329x+19.6),

the line segment C′C is represented by coordinates (x,0.0067x²−0.6034x+79.729, −0.0067x²−0.3966x+20.271), and

the line segments BD, CO, and OA are straight lines.

When the requirements above are satisfied, the refrigerant according tothe present disclosure has a refrigerating capacity ratio of 85% or morerelative to that of R410A, and a COP of 92.5% or more relative to thatof R410A.

When the mass % of HFO-1132(E), HFO-1123, and R1234yf, based on theirsum in the refrigerant A according to the present disclosure isrespectively represented by x, y, and z, the refrigerant is preferably arefrigerant wherein coordinates (x,y,z) in a ternary composition diagramin which the sum of HFO-1132(E), HFO-1123, and R1234yf is 100 mass % arewithin a figure surrounded by line segments GI, IA, AA′, A′B, BD, DC′,C′C, and CG that connect the following 8 points:

point G (72.0, 28.0, 0.0),

point I (72.0, 0.0, 28.0),

point A (68.6, 0.0, 31.4),

point A′ (30.6, 30.0, 39.4),

point B (0.0, 58.7, 41.3),

point D (0.0, 80.4, 19.6),

point C′ (19.5, 70.5, 10.0), and

point C (32.9, 67.1, 0.0),

or on the above line segments (excluding the points on the line segmentCG);

the line segment AA′ is represented by coordinates (x,0.0016x²−0.9473x+57.497, −0.0016x²−0.0527x+42.503),

the line segment A′B is represented by coordinates (x,0.0029x²−1.0268x+58.7, −0.0029x²+0.0268x+41.3),

the line segment DC′ is represented by coordinates (x,0.0082x²−0.6671x+80.4, −0.0082x²−0.3329x+19.6),

the line segment C′C is represented by coordinates (x,0.0067x²−0.6034x+79.729, −0.0067x²−0.3966x+20.271), and

the line segments GI, IA, BD, and CG are straight lines.

When the requirements above are satisfied, the refrigerant A accordingto the present disclosure has a refrigerating capacity ratio of 85% ormore relative to that of R410A, and a COP of 92.5% or more relative tothat of R410A; furthermore, the refrigerant A has a WCF lowerflammability according to the ASHRAE Standard (the WCF composition has aburning velocity of 10 cm/s or less).

When the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumin the refrigerant according to the present disclosure is respectivelyrepresented by x, y, and z, the refrigerant is preferably a refrigerantwherein coordinates (x,y,z) in a ternary composition diagram in whichthe sum of HFO-1132(E), HFO-1123, and R1234yf is 100 mass % are withinthe range of a figure surrounded by line segments JP, PN, NK, KA′, A′B,BD, DC′, C′C, and CJ that connect the following 9 points:

point J (47.1, 52.9, 0.0),

point P (55.8, 42.0, 2.2),

point N (68.6, 16.3, 15.1),

point K (61.3, 5.4, 33.3),

point A′ (30.6, 30.0, 39.4),

point B (0.0, 58.7, 41.3),

point D (0.0, 80.4, 19.6),

point C′ (19.5, 70.5, 10.0), and

point C (32.9, 67.1, 0.0),

or on the above line segments (excluding the points on the line segmentCJ);

the line segment PN is represented by coordinates (x,−0.1135x²+12.112x−280.43, 0.1135x²−13.112x+380.43),

the line segment NK is represented by coordinates (x,0.2421x²−29.955x+931.91, −0.2421x²+28.955x−831.91),

the line segment KA′ is represented by coordinates (x,0.0016x²−0.9473x+57.497, −0.0016x²−0.0527x+42.503),

the line segment A′B is represented by coordinates (x,0.0029x²−1.0268x+58.7, −0.0029x²+0.0268x+41.3),

the line segment DC′ is represented by coordinates (x,0.0082x²−0.6671x+80.4, −0.0082x²−0.3329x+19.6),

the line segment C′C is represented by coordinates (x,0.0067x²−0.6034x+79.729, −0.0067x²−0.3966x+20.271), and

the line segments JP, BD, and CG are straight lines.

When the requirements above are satisfied, the refrigerant A accordingto the present disclosure has a refrigerating capacity ratio of 85% ormore relative to that of R410A, and a COP of 92.5% or more relative tothat of R410A; furthermore, the refrigerant exhibits a lowerflammability (Class 2L) according to the ASHRAE Standard (the WCFcomposition and the WCFF composition have a burning velocity of 10 cm/sor less).

When the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumin the refrigerant according to the present disclosure is respectivelyrepresented by x, y, and z, the refrigerant is preferably a refrigerantwherein coordinates (x,y,z) in a ternary composition diagram in whichthe sum of HFO-1132(E), HFO-1123, and R1234yf is 100 mass % are withinthe range of a figure surrounded by line segments JP, PL, LM, MA′, A′B,BD, DC′, C′C, and CJ that connect the following 9 points:

point J (47.1, 52.9, 0.0),

point P (55.8, 42.0, 2.2),

point L (63.1, 31.9, 5.0),

point M (60.3, 6.2, 33.5),

point A′ (30.6, 30.0, 39.4),

point B (0.0, 58.7, 41.3),

point D (0.0, 80.4, 19.6),

point C′ (19.5, 70.5, 10.0), and

point (32.9, 67.1, 0.0),

or on the above line segments (excluding the points on the line segmentCJ);

the line segment PL is represented by coordinates (x,−0.1135x²+12.112x−280.43, 0.1135x²−13.112x+380.43),

the line segment MA′ is represented by coordinates (x,0.0016x²−0.9473x+57.497, −0.0016x²−0.0527x+42.503),

the line segment A′B is represented by coordinates (x,0.0029x²−1.0268x+58.7, −0.0029x²+0.0268x+41.3),

the line segment DC′ is represented by coordinates (x,0.0082x²−0.6671x+80.4, −0.0082x²−0.3329x+19.6),

the line segment C′C is represented by coordinates (x,0.0067x²−0.6034x+79.729, −0.0067x²−0.3966x+20.271), and

the line segments JP, LM, BD, and CG are straight lines.

When the requirements above are satisfied, the refrigerant according tothe present disclosure has a refrigerating capacity ratio of 85% or morerelative to that of R410A, and a COP of 92.5% or more relative to thatof R410A; furthermore, the refrigerant has an RCL of 40 g/m³ or more.

When the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumin the refrigerant A according to the present disclosure is respectivelyrepresented by x, y, and z, the refrigerant is preferably a refrigerantwherein coordinates (x,y,z) in a ternary composition diagram in whichthe sum of HFO-1132(E), HFO-1123, and R1234yf is 100 mass % are withinthe range of a figure surrounded by line segments PL, LM, MA′, A′B, BF,FT, and TP that connect the following 7 points:

point P (55.8, 42.0, 2.2),

point L (63.1, 31.9, 5.0),

point M (60.3, 6.2, 33.5),

point A′ (30.6, 30.0, 39.4),

point B (0.0, 58.7, 41.3),

point F (0.0, 61.8, 38.2), and

point T (35.8, 44.9, 19.3),

or on the above line segments (excluding the points on the line segmentBF);

the line segment PL is represented by coordinates (x,−0.1135x²+12.112x−280.43, 0.1135x²−13.112x+380.43),

the line segment MA′ is represented by coordinates (x,0.0016x²−0.9473x+57.497, −0.0016x²−0.0527x+42.503),

the line segment A′B is represented by coordinates (x,0.0029x²−1.0268x+58.7, −0.0029x²+0.0268x+41.3),

the line segment FT is represented by coordinates (x,0.0078x²−0.7501x+61.8, −0.0078x²−0.2499x+38.2),

the line segment TP is represented by coordinates (x,0.00672x²−0.7607x+63.525, −0.00672x²−0.2393x+36.475), and

the line segments LM and BF are straight lines.

When the requirements above are satisfied, the refrigerant according tothe present disclosure has a refrigerating capacity ratio of 85% or morerelative to that of R410A, and a COP of 95% or more relative to that ofR410A; furthermore, the refrigerant has an RCL of 40 g/m³ or more.

The refrigerant A according to the present disclosure is preferably arefrigerant wherein when the mass % of HFO-1132(E), HFO-1123, andR1234yf based on their sum in the refrigerant is respectivelyrepresented by x, y, and z, coordinates (x,y,z) in a ternary compositiondiagram in which the sum of HFO-1132(E), HFO-1123, and R1234yf is 100mass % are within the range of a figure surrounded by line segments PL,LQ, QR, and RP that connect the following 4 points:

point P (55.8, 42.0, 2.2),

point L (63.1, 31.9, 5.0),

point Q (62.8, 29.6, 7.6), and

point R (49.8, 42.3, 7.9),

or on the above line segments;

the line segment PL is represented by coordinates (x,−0.1135x²+12.112x−280.43, 0.1135x²−13.112x+380.43),

the line segment RP is represented by coordinates (x,0.00672x²−0.7607x+63.525, −0.00672x²−0.2393x+36.475), and

the line segments LQ and QR are straight lines.

When the requirements above are satisfied, the refrigerant according tothe present disclosure has a COP of 95% or more relative to that ofR410A, and an RCL of 40 g/m³ or more, furthermore, the refrigerant has acondensation temperature glide of 1° C. or less.

The refrigerant A according to the present disclosure is preferably arefrigerant wherein when the mass % of HFO-1132(E), HFO-1123, andR1234yf based on their sum in the refrigerant is respectivelyrepresented by x, y, and z, coordinates (x,y,z) in a ternary compositiondiagram in which the sum of HFO-1132(E), HFO-1123, and R1234yf is 100mass % are within the range of a figure surrounded by line segments SM,MA′, A′B, BF, FT, and TS that connect the following 6 points:

point S (62.6, 28.3, 9.1),

point M (60.3, 6.2, 33.5),

point A′ (30.6, 30.0, 39.4),

point B (0.0, 58.7, 41.3),

point F (0.0, 61.8, 38.2), and

point T (35.8, 44.9, 19.3),

or on the above line segments,

the line segment MA′ is represented by coordinates (x,0.0016x²−0.9473x+57.497, −0.0016x²−0.0527x+42.503),

the line segment A′B is represented by coordinates (x,0.0029x²−1.0268x+58.7, −0.0029x²+0.0268x+41.3),

the line segment FT is represented by coordinates (x,0.0078x²−0.7501x+61.8, −0.0078x²−0.2499x+38.2),

the line segment TS is represented by coordinates (x,−0.0017x²−0.7869x+70.888, −0.0017x²−0.2131x+29.112), and

the line segments SM and BF are straight lines.

When the requirements above are satisfied, the refrigerant according tothe present disclosure has a refrigerating capacity ratio of 85% or morerelative to that of R410A, a COP of 95% or more relative to that ofR410A, and an RCL of 40 g/m³ or more furthermore, the refrigerant has adischarge pressure of 105% or more relative to that of R410A.

The refrigerant A according to the present disclosure is preferably arefrigerant wherein when the mass % of HFO-1132(E), HFO-1123, andR1234yf based on their sum in the refrigerant is respectivelyrepresented by x, y, and z, coordinates (x,y,z) in a ternary compositiondiagram in which the sum of HFO-1132(E), HFO-1123, and R1234yf is 100mass % are within the range of a figure surrounded by line segments Od,dg, gh, and hO that connect the following 4 points:

point d (87.6, 0.0, 12.4),

point g (18.2, 55.1, 26.7),

point h (56.7, 43.3, 0.0), and

point o (100.0, 0.0, 0.0),

or on the line segments Od, dg, gh, and hO (excluding the points O andh);

the line segment dg is represented by coordinates(0.0047y²−1.5177y+87.598, y, −0.0047y²+0.5177y+12.402),

the line segment gh is represented by coordinates(−0.0134z²−1.0825z+56.692, 0.0134z²+0.0825z+43.308, z), and

the line segments hO and Od are straight lines.

When the requirements above are satisfied, the refrigerant according tothe present disclosure has a refrigerating capacity ratio of 92.5% ormore relative to that of R410A, and a COP ratio of 92.5% or morerelative to that of R410A.

The refrigerant A according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R1234yf, based on theirsum is respectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), HFO-1123,and R1234yf is 100 mass % are within the range of a figure surrounded byline segments lg, gh, hi, and il that connect the following 4 points:

point l (72.5, 10.2, 17.3),

point g (18.2, 55.1, 26.7),

point h (56.7, 43.3, 0.0), and

point i (72.5, 27.5, 0.0) or on the line segments lg, gh, and il(excluding the points h and i);

the line segment lg is represented by coordinates(0.0047y²−1.5177y+87.598, y, −0.0047y²+0.5177y+12.402),

the line gh is represented by coordinates (−0.0134z²−1.0825z+56.692,0.0134z²+0.0825z+43.308, z), and

the line segments hi and il are straight lines.

When the requirements above are satisfied, the refrigerant according tothe present disclosure has a refrigerating capacity ratio of 92.5% ormore relative to that of R410A, and a COP ratio of 92.5% or morerelative to that of R410A; furthermore, the refrigerant has a lowerflammability (Class 2L) according to the ASHRAE Standard.

The refrigerant A according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumis respectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), HFO-1123,and R1234yf is 100 mass % are within the range of a figure surrounded byline segments Od, de, ef, and fO that connect the following 4 points:

point d (87.6, 0.0, 12.4),

point e (31.1, 42.9, 26.0),

point f (65.5, 34.5, 0.0), and

point O (100.0, 0.0, 0.0),

or on the line segments Od, de, and ef (excluding the points O and f);

the line segment de is represented by coordinates(0.0047y²−1.5177y+87.598, y, −0.0047y²+0.5177y+12.402),

the line segment ef is represented by coordinates(−0.0064z²−1.1565z+65.501, 0.0064z²+0.1565z+34.499, z), and

the line segments fO and Od are straight lines.

When the requirements above are satisfied, the refrigerant according tothe present disclosure has a refrigerating capacity ratio of 93.5% ormore relative to that of R410A, and a COP ratio of 93.5% or morerelative to that of R410A.

The refrigerant A according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumis respectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), HFO-1123,and R1234yf is 100 mass % are within the range of a figure surrounded byline segments le, ef, fi, and il that connect the following 4 points:

point l (72.5, 10.2, 17.3),

point e (31.1, 42.9, 26.0),

point f (65.5, 34.5, 0.0), and

point i (72.5, 27.5, 0.0),

or on the line segments le, ef, and il (excluding the points f and i);

the line segment le is represented by coordinates(0.0047y²−1.5177y+87.598, y, −0.0047y²+0.5177y+12.402),

the line segment ef is represented by coordinates(−0.0134z²−1.0825z+56.692, 0.0134z²+0.0825z+43.308, z), and

the line segments fi and il are straight lines.

When the requirements above are satisfied, the refrigerant according tothe present disclosure has a refrigerating capacity ratio of 93.5% ormore relative to that of R410A, and a COP ratio of 93.5% or morerelative to that of R410A; furthermore, the refrigerant has a lowerflammability (Class 2L) according to the ASHRAE Standard.

The refrigerant A according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumis respectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), HFO-1123,and R1234yf is 100 mass % are within the range of a figure surrounded byline segments Oa, ab, bc, and cO that connect the following 4 points:

point a (93.4, 0.0, 6.6),

point b (55.6, 26.6, 17.8),

point c (77.6, 22.4, 0.0), and

point O (100.0, 0.0, 0.0),

or on the line segments Oa, ab, and bc (excluding the points O and c);

the line segment ab is represented by coordinates(0.0052y²−1.5588y+93.385, y, −0.0052y²+0.5588y+6.615),

the line segment be is represented by coordinates(−0.0032z²−1.1791z+77.593, 0.0032z²+0.1791z+22.407, z), and

the line segments cO and Oa are straight lines.

When the requirements above are satisfied, the refrigerant according tothe present disclosure has a refrigerating capacity ratio of 95% or morerelative to that of R410A, and a COP ratio of 95% or more relative tothat of R410A.

The refrigerant A according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumis respectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), HFO-1123,and R1234yf is 100 mass % are within the range of a figure surrounded byline segments kb, bj, and jk that connect the following 3 points:

point k (72.5, 14.1, 13.4),

point b (55.6, 26.6, 17.8), and

point j (72.5, 23.2, 4.3),

or on the line segments kb, bj, and jk;

the line segment kb is represented by coordinates(0.0052y²−1.5588y+93.385, y, and −0.0052y²+0.5588y+6.615),

the line segment bj is represented by coordinates(−0.0032z²−1.1791z+77.593, 0.0032z²+0.1791z+22.407, z), and

the line segment jk is a straight line.

When the requirements above are satisfied, the refrigerant according tothe present disclosure has a refrigerating capacity ratio of 95% or morerelative to that of R410A, and a COP ratio of 95% or more relative tothat of R410A; furthermore, the refrigerant has a lower flammability(Class 2L) according to the ASHRAE Standard.

The refrigerant according to the present disclosure may further compriseother additional refrigerants in addition to HFO-1132(E), HFO-1123, andR1234yf, as long as the above properties and effects are not impaired.In this respect, the refrigerant according to the present disclosurepreferably comprises HFO-1132(E), HFO-1123, and R1234yf in a totalamount of 99.5 mass % or more, more preferably 99.75 mass % or more, andstill more preferably 99.9 mass % or more, based on the entirerefrigerant.

The refrigerant according to the present disclosure may compriseHFO-1132(E), HFO-1123, and R1234yf in a total amount of 99.5 mass % ormore, 99.75 mass % or more, or 99.9 mass % or more, based on the entirerefrigerant.

Additional refrigerants are not particularly limited and can be widelyselected.

The mixed refrigerant may contain one additional refrigerant, or two ormore additional refrigerants.

(Examples of Refrigerant A)

The present disclosure is described in more detail below with referenceto Examples of refrigerant A. However, refrigerant A is not limited tothe Examples.

The GWP of R1234yf and a composition consisting of a mixed refrigerantR410A (R32=50%/R125=50%) was evaluated based on the values stated in theIntergovernmental Panel on Climate Change (IPCC), fourth report. The GWPof HFO-1132(E), which was not stated therein, was assumed to be 1 fromHFO-1132a (GWP=1 or less) and HFO-1123 (GWP=0.3, described in PatentLiterature 1). The refrigerating capacity of R410A and compositions eachcomprising a mixture of HFO-1132(E), HFO-1123, and R1234yf wasdetermined by performing theoretical refrigeration cycle calculationsfor the mixed refrigerants using the National Institute of Science andTechnology (NIST) and Reference Fluid Thermodynamic and TransportProperties Database (Refprop 9.0) under the following conditions.

Further, the RCL of the mixture was calculated with the LFL ofHFO-1132(E) being 4.7 vol. %, the LFL of HFO-1123 being 10 vol. %, andthe LFL of R1234yf being 6.2 vol. %, in accordance with the ASHRAEStandard 34-2013.

Evaporating temperature: 5° C.

Condensation temperature: 45° C.

Degree of superheating: 5 K

Degree of subcooling: 5 K

Compressor efficiency: 70%

Tables 1 to 34 show these values together with the GWP of each mixedrefrigerant.

TABLE 1 Comp. Comp. Example Comp. Comp. Ex. 2 Ex. 3 Example 2 ExampleEx. 4 Item Unit Ex. 1 O A 1 A′ 3 B HFO-1132(E) mass % R410A 100.0 68.649.0 30.6 14.1 0.0 HFO-1123 mass % 0.0 0.0 14.9 30.0 44.8 58.7 R1234yfmass % 0.0 31.4 36.1 39.4 41.1 41.3 GWP — 2088 1 2 2 2 2 2 COP ratio %(relative 100 99.7 100.0 98.6 97.3 96.3 95.5 to 410A) Refrigerating %(relative 100 98.3 85.0 85.0 85.0 85.0 85.0 capacity ratio to 410A)Condensation ° C. 0.1 0.00 1.98 3.36 4.46 5.15 5.35 glide Discharge %(relative 100.0 99.3 87.1 88.9 90.6 92.1 93.2 pressure to 410A) RCL g/m³— 30.7 37.5 44.0 52.7 64.0 78.6

TABLE 2 Comp. Example Comp. Comp. Example Comp. Ex. 5 Example 5 ExampleEx. 6 Ex. 7 7 Ex. 8 Item Unit C 4 C′ 6 D E E′ F HFO-1132(E) mass % 32.926.6 19.5 10.9 0.0 58.0 23.4 0.0 HFO-1123 mass % 67.1 68.4 70.5 74.180.4 42.0 48.5 61.8 R1234yf mass % 0.0 5.0 10.0 15.0 19.6 0.0 28.1 38.2GWP — 1 1 1 1 2 1 2 2 COP ratio % (relative 92.5 92.5 92.5 92.5 92.595.0 95.0 95.0 to 410A) Refrigerating % (relative 107.4 105.2 102.9100.5 97.9 105.0 92.5 86.9 capacity ratio to 410A) Condensation ° C.0.16 0.52 0.94 1.42 1.90 0.42 3.16 4.80 glide Discharge % (relative119.5 117.4 115.3 113.0 115.9 112.7 101.0 95.8 pressure to 410A) RCLg/m³ 53.5 57.1 62.0 69.1 81.3 41.9 46.3 79.0

TABLE 3 Comp. Example Example Example Example Example Ex. 9 8 9 10 11 12Item Unit J P L N N′ K HFO-1132(E) mass % 47.1 55.8 63.1 68.6 65.0 61.3HFO-1123 mass % 52.9 42.0 31.9 16.3 7.7 5.4 R1234yf mass % 0.0 2.2 5.015.1 27.3 33.3 GWP — 1 1 1 1 2 2 COP ratio % (relative 93.8 95.0 96.197.9 99.1 99.5 to 410A) Refrigerating % (relative 106.2 104.1 101.6 95.088.2 85.0 capacity ratio to 410A) Condensation ° C. 0.31 0.57 0.81 1.412.11 2.51 glide Discharge % (relative 115.8 111.9 107.8 99.0 91.2 87.7pressure to 410A) RCL g/m³ 46.2 42.6 40.0 38.0 38.7 39.7

TABLE 4 Example Example Example Example Example Example Example 13 14 1516 17 18 19 Item Unit L M Q R S S′ T HFO-1132(E) mass % 63.1 60.3 62.849.8 62.6 50.0 35.8 HFO-1123 mass % 31.9 6.2 29.6 42.3 28.3 35.8 44.9R1234yf mass % 5.0 33.5 7.6 7.9 9.1 14.2 19.3 GWP — 1 2 1 1 1 1 2 COPratio % (relative 96.1 99.4 96.4 95.0 96.6 95.8 95.0 to 410A)Refrigerating % (relative 101.6 85.0 100.2 101.7 99.4 98.1 96.7 capacityratio to 410A) Condensation ° C. 0.81 2.58 1.00 1.00 1.10 1.55 2.07glide Discharge % (relative 107.8 87.9 106.0 109.6 105.0 105.0 105.0pressure to 410A) RCL g/m³ 40.0 40.0 40.0 44.8 40.0 44.4 50.8

TABLE 5 Comp. Ex. 10 Example 20 Example 21 Item Unit G H I HFO-1132(E)mass % 72.0 72.0 72.0 HFO-1123 mass % 28.0 14.0 0.0 R1234yf mass % 0.014.0 28.0 GWP — 1 1 2 COP ratio % (relative 96.6 98.2 99.9 to 410A)Refrigerating % (relative 103.1 95.1 86.6 capacity ratio to 410A)Condensation glide ° C. 0.46 1.27 1.71 Discharge pressure % (relative108.4 98.7 88.6 to 410A) RCL g/m³ 37.4 37.0 36.6

TABLE 6 Comp. Comp. Example Example Example Example Example Comp. ItemUnit Ex. 11 Ex. 12 22 23 24 25 26 Ex. 13 HFO-1132(E) mass % 10.0 20.030.0 40.0 50.0 60.0 70.0 80.0 HFO-1123 mass % 85.0 75.0 65.0 55.0 45.035.0 25.0 15.0 R1234yf mass % 5.0 5.0 5.0 5.0 5.0 5.0 5.0 5.0 GWP — 1 11 1 1 1 1 1 COP ratio % (relative 91.4 92.0 92.8 93.7 94.7 95.8 96.998.0 to 410A) Refrigerating % (relative 105.7 105.5 105.0 104.3 103.3102.0 100.6 99.1 capacity ratio to 410A) Condensation ° C. 0.40 0.460.55 0.66 0.75 0.80 0.79 0.67 glide Discharge % (relative 120.1 118.7116.7 114.3 111.6 108.7 105.6 102.5 pressure to 410A) RCL g/m³ 71.0 61.954.9 49.3 44.8 41.0 37.8 35.1

TABLE 7 Comp. Example Example Example Example Example Example Comp. ItemUnit Ex. 14 27 28 29 30 31 32 Ex. 15 HFO-1132(E) mass % 10.0 20.0 30.040.0 50.0 60.0 70.0 80.0 HFO-1123 mass % 80.0 70.0 60.0 50.0 40.0 30.020.0 10.0 R1234yf mass % 10.0 10.0 10.0 10.0 10.0 10.0 10.0 10.0 GWP — 11 1 1 1 1 1 1 COP ratio % (relative 91.9 92.5 93.3 94.3 95.3 96.4 97.598.6 to 410A) Refrigerating % (relative 103.2 102.9 102.4 101.5 100.599.2 97.8 96.2 capacity ratio to 410A) Condensation ° C. 0.87 0.94 1.031.12 1.18 1.18 1.09 0.88 glide Discharge % (relative 116.7 115.2 113.2110.8 108.1 105.2 102.1 99.0 pressure to 410A) RCL g/m³ 70.5 61.6 54.649.1 44.6 40.8 37.7 35.0

TABLE 8 Comp. Example Example Example Example Example Example Comp. ItemUnit Ex. 16 33 34 35 36 37 38 Ex. 17 HFO-1132(E) mass % 10.0 20.0 30.040.0 50.0 60.0 70.0 80.0 HFO-1123 mass % 75.0 65.0 55.0 45.0 35.0 25.015.0 5.0 R1234yf mass % 15.0 15.0 15.0 15.0 15.0 15.0 15.0 15.0 GWP — 11 1 1 1 1 1 1 COP ratio % (relative 92.4 93.1 93.9 94.8 95.9 97.0 98.199.2 to 410A) Refrigerating % (relative 100.5 100.2 99.6 98.7 97.7 96.494.9 93.2 capacity ratio to 410A) Condensation ° C. 1.41 1.49 1.56 1.621.63 1.55 1.37 1.05 glide Discharge % (relative 113.1 111.6 109.6 107.2104.5 101.6 98.6 95.5 pressure to 410A) RCL g/m³ 70.0 61.2 54.4 48.944.4 40.7 37.5 34.8

TABLE 9 Example Example Example Example Example Example Example ItemUnit 39 40 41 42 43 44 45 HFO-1132(E) mass % 10.0 20.0 30.0 40.0 50.060.0 70.0 HFO-1123 mass % 70.0 60.0 50.0 40.0 30.0 20.0 10.0 R1234yfmass % 20.0 20.0 20.0 20.0 20.0 20.0 20.0 GWP — 2 2 2 2 2 2 2 COP ratio% (relative 93.0 93.7 94.5 95.5 96.5 97.6 98.7 to 410A) Refrigerating %(relative 97.7 97.4 96.8 95.9 94.7 93.4 91.9 capacity ratio to 410A)Condensation ° C. 2.03 2.09 2.13 2.14 2.07 1.91 1.61 glide Discharge %(relative 109.4 107.9 105.9 103.5 100.8 98.0 95.0 pressure to 410A) RCLg/m³ 69.6 60.9 54.1 48.7 44.2 40.5 37.4

TABLE 10 Example Example Example Example Example Example Example ItemUnit 46 47 48 49 50 51 52 HFO-1132(E) mass % 10.0 20.0 30.0 40.0 50.060.0 70.0 HFO-1123 mass % 65.0 55.0 45.0 35.0 25.0 15.0 5.0 R1234yf mass% 25.0 25.0 25.0 25.0 25.0 25.0 25.0 GWP — 2 2 2 2 2 2 2 COP ratio %(relative 93.6 94.3 95.2 96.1 97.2 98.2 99.3 to 410A) Refrigerating %(relative 94.8 94.5 93.8 92.9 91.8 90.4 88.8 capacity ratio to 410A)Condensation ° C. 2.71 2.74 2.73 2.66 2.50 2.22 1.78 glide Discharge %(relative 105.5 104.0 102.1 99.7 97.1 94.3 91.4 pressure to 410A) RCLg/m³ 69.1 60.5 53.8 48.4 44.0 40.4 37.3

TABLE 11 Example Example Example Example Example Example Item Unit 53 5455 56 57 58 HFO-1132(E) mass % 10.0 20.0 30.0 40.0 50.0 60.0 HFO-1123mass % 60.0 50.0 40.0 30.0 20.0 10.0 R1234yf mass % 30.0 30.0 30.0 30.030.0 30.0 GWP — 2 2 2 2 2 2 COP ratio % (relative 94.3 95.0 95.9 96.897.8 98.9 to 410A) Refrigerating % (relative 91.9 91.5 90.8 89.9 88.787.3 capacity ratio to 410A) Condensation ° C. 3.46 3.43 3.35 3.18 2.902.47 glide Discharge % (relative 101.6 100.1 98.2 95.9 93.3 90.6pressure to 410A) RCL g/m³ 68.7 60.2 53.5 48.2 43.9 40.2

TABLE 12 Example Example Example Example Example Comp. Item Unit 59 6061 62 63 Ex. 18 HFO-1132(E) mass % 10.0 20.0 30.0 40.0 50.0 60.0HFO-1123 mass % 55.0 45.0 35.0 25.0 15.0 5.0 R1234yf mass % 35.0 35.035.0 35.0 35.0 35.0 GWP — 2 2 2 2 2 2 COP ratio % (relative 95.0 95.896.6 97.5 98.5 99.6 to 410A) Refrigerating % (relative 88.9 88.5 87.886.8 85.6 84.1 capacity ratio to 410A) Condensation ° C. 4.24 4.15 3.963.67 3.24 2.64 glide Discharge % (relative 97.6 96.1 94.2 92.0 89.5 86.8pressure to 410A) RCL g/m³ 68.2 59.8 53.2 48.0 43.7 40.1

TABLE 13 Example Example Comp. Comp. Comp. Item Unit 64 65 Ex. 19 Ex. 20Ex. 21 HFO-1132(E) mass % 10.0 20.0 30.0 40.0 50.0 HFO-1123 mass % 50.040.0 30.0 20.0 10.0 R1234yf mass % 40.0 40.0 40.0 40.0 40.0 GWP — 2 2 22 2 COP ratio % (relative 95.9 96.6 97.4 98.3 99.2 to 410A)Refrigerating % (relative 85.8 85.4 84.7 83.6 82.4 capacity ratio to410A) Condensation ° C. 5.05 4.85 4.55 4.10 3.50 glide Discharge %(relative 93.5 92.1 90.3 88.1 85.6 pressure to 410A) RCL g/m³ 67.8 59.553.0 47.8 43.5

TABLE 14 Example Example Example Example Example Example Example ExampleItem Unit 66 67 68 69 70 71 72 73 HFO-1132(E) mass % 54.0 56.0 58.0 62.052.0 54.0 56.0 58.0 HFO-1123 mass % 41.0 39.0 37.0 33.0 41.0 39.0 37.035.0 R1234yf mass % 5.0 5.0 5.0 5.0 7.0 7.0 7.0 7.0 GWP — 1 1 1 1 1 1 11 COP ratio % (relative 95.1 95.3 95.6 96.0 95.1 95.4 95.6 95.8 to 410A)Refrigerating % (relative 102.8 102.6 102.3 101.8 101.9 101.7 101.5101.2 capacity ratio to 410A) Condensation ° C. 0.78 0.79 0.80 0.81 0.930.94 0.95 0.95 glide Discharge % (relative 110.5 109.9 109.3 108.1 109.7109.1 108.5 107.9 pressure to 410A) RCL g/m³ 43.2 42.4 41.7 40.3 43.943.1 42.4 41.6

TABLE 15 Example Example Example Example Example Example Example ExampleItem Unit 74 75 76 77 78 79 80 81 HFO-1132(E) mass % 60.0 62.0 61.0 58.060.0 62.0 52.0 54.0 HFO-1123 mass % 33.0 31.0 29.0 30.0 28.0 26.0 34.032.0 R1234yf mass % 7.0 7.0 10.0 12.0 12.0 12.0 14.0 14.0 GWP — 1 1 1 11 1 1 1 COP ratio % (relative 96.0 96.2 96.5 96.4 96.6 96.8 96.0 96.2 to410A) Refrigerating % (relative 100.9 100.7 99.1 98.4 98.1 97.8 98.097.7 capacity ratio to 410A) Condensation ° C. 0.95 0.95 1.18 1.34 1.331.32 1.53 1.53 glide Discharge % (relative 107.3 106.7 104.9 104.4 103.8103.2 104.7 104.1 pressure to 410A) RCL g/m³ 40.9 40.3 40.5 41.5 40.840.1 43.6 42.9

TABLE 16 Example Example Example Example Example Example Example ExampleItem Unit 82 83 84 85 86 87 88 89 HFO-1132(E) mass % 56.0 58.0 60.0 48.050.0 52.0 54.0 56.0 HFO-1123 mass % 30.0 28.0 26.0 36.0 34.0 32.0 30.028.0 R1234yf mass % 14.0 14.0 14.0 16.0 16.0 16.0 16.0 16.0 GWP — 1 1 11 1 1 1 1 COP ratio % (relative 96.4 96.6 96.9 95.8 96.0 96.2 96.4 96.7to 410A) Refrigerating % (relative 97.5 97.2 96.9 97.3 97.1 96.8 96.696.3 capacity ratio to 410A) Condensation ° C. 1.51 1.50 1.48 1.72 1.721.71 1.69 1.67 glide Discharge % (relative 103.5 102.9 102.3 104.3 103.8103.2 102.7 102.1 pressure to 410A) RCL g/m³ 42.1 41.4 40.7 45.2 44.443.6 42.8 42.1

TABLE 17 Example Example Example Example Example Example Example ExampleItem Unit 90 91 92 93 94 95 96 97 HFO-1132(E) mass % 58.0 60.0 42.0 44.046.0 48.0 50.0 52.0 HFO-1123 mass % 26.0 24.0 40.0 38.0 36.0 34.0 32.030.0 R1234yf mass % 16.0 16.0 18.0 18.0 18.0 18.0 18.0 18.0 GWP — 1 1 22 2 2 2 2 COP ratio % (relative 96.9 97.1 95.4 95.6 95.8 96.0 96.3 96.5to 410A) Refrigerating % (relative 96.1 95.8 96.8 96.6 96.4 96.2 95.995.7 capacity ratio to 410A) Condensation ° C. 1.65 1.63 1.93 1.92 1.921.91 1.89 1.88 glide Discharge % (relative 101.5 100.9 104.5 103.9 103.4102.9 102.3 101.8 pressure to 410A) RCL g/m³ 41.4 40.7 47.8 46.9 46.045.1 44.3 43.5

TABLE 18 Example Example Example Example Example Example Example ExampleItem Unit 98 99 100 101 102 103 104 105 HFO-1132(E) mass % 54.0 56.058.0 60.0 36.0 38.0 42.0 44.0 HFO-1123 mass % 28.0 26.0 24.0 22.0 44.042.0 38.0 36.0 R1234yf mass % 18.0 18.0 18.0 18.0 20.0 20.0 20.0 20.0GWP — 2 2 2 2 2 2 2 2 COP ratio % (relative 96.7 96.9 97.1 97.3 95.195.3 95.7 95.9 to 410A) Refrigerating % (relative 95.4 95.2 94.9 94.696.3 96.1 95.7 95.4 capacity ratio to 410A) Condensation ° C. 1.86 1.831.80 1.77 2.14 2.14 2.13 2.12 glide Discharge % (relative 101.2 100.6100.0 99.5 104.5 104.0 103.0 102.5 pressure to 410A) RCL g/m³ 42.7 42.041.3 40.6 50.7 49.7 47.7 46.8

TABLE 19 Example Example Example Example Example Example Example ExampleItem Unit 106 107 108 109 110 111 112 113 HFO-1132(E) mass % 46.0 48.052.0 54.0 56.0 58.0 34.0 36.0 HFO-1123 mass % 34.0 32.0 28.0 26.0 24.022.0 44.0 42.0 R1234yf mass % 20.0 20.0 20.0 20.0 20.0 20.0 22.0 22.0GWP — 2 2 2 2 2 2 2 2 COP ratio % (relative 96.1 96.3 96.7 96.9 97.297.4 95.1 95.3 to 410A) Refrigerating % (relative 95.2 95.0 94.5 94.294.0 93.7 95.3 95.1 capacity ratio to 410A) Condensation ° C. 2.11 2.092.05 2.02 1.99 1.95 2.37 2.36 glide Discharge % (relative 101.9 101.4100.3 99.7 99.2 98.6 103.4 103.0 pressure to 410A) RCL g/m³ 45.9 45.043.4 42.7 41.9 41.2 51.7 50.6

TABLE 20 Example Example Example Example Example Example Example ExampleItem Unit 114 115 116 117 118 119 120 121 HFO-1132(E) mass % 38.0 40.042.0 44.0 46.0 48.0 50.0 52.0 HFO-1123 mass % 40.0 38.0 36.0 34.0 32.030.0 28.0 26.0 R1234yf mass % 22.0 22.0 22.0 22.0 22.0 22.0 22.0 22.0GWP — 2 2 2 2 2 2 2 2 COP ratio % (relative 95.5 95.7 95.9 96.1 96.496.6 96.8 97.0 to 410A) Refrigerating % (relative 94.9 94.7 94.5 94.394.0 93.8 93.6 93.3 capacity ratio to 410A) Condensation ° C. 2.36 2.352.33 2.32 2.30 2.27 2.25 2.21 glide Discharge % (relative 102.5 102.0101.5 101.0 100.4 99.9 99.4 98.8 pressure to 410A) RCL g/m³ 49.6 48.647.6 46.7 45.8 45.0 44.1 43.4

TABLE 21 Example Example Example Example Example Example Example ExampleItem Unit 122 123 124 125 126 127 128 129 HFO-1132(E) mass % 54.0 56.058.0 60.0 32.0 34.0 36.0 38.0 HFO-1123 mass % 24.0 22.0 20.0 18.0 44.042.0 40.0 38.0 R1234yf mass % 22.0 22.0 22.0 22.0 24.0 24.0 24.0 24.0GWP — 2 2 2 2 2 2 2 2 COP ratio % (relative 97.2 97.4 97.6 97.9 95.295.4 95.6 95.8 to 410A) Refrigerating % (relative 93.0 92.8 92.5 92.294.3 94.1 93.9 93.7 capacity ratio to 410A) Condensation ° C. 2.18 2.142.09 2.04 2.61 2.60 2.59 2.58 glide Discharge % (relative 98.2 97.7 97.196.5 102.4 101.9 101.5 101.0 pressure to 410A) RCL g/m³ 42.6 41.9 41.240.5 52.7 51.6 50.5 49.5

TABLE 22 Example Example Example Example Example Example Example ExampleItem Unit 130 131 132 133 134 135 136 137 HFO-1132(E) mass % 40.0 42.044.0 46.0 48.0 50.0 52.0 54.0 HFO-1123 mass % 36.0 34.0 32.0 30.0 28.026.0 24.0 22.0 R1234yf mass % 24.0 24.0 24.0 24.0 24.0 24.0 24.0 24.0GWP — 2 2 2 2 2 2 2 2 COP ratio % (relative 96.0 96.2 96.4 96.6 96.897.0 97.2 97.5 to 410A) Refrigerating % (relative 93.5 93.3 93.1 92.892.6 92.4 92.1 91.8 capacity ratio to 410A) Condensation ° C. 2.56 2.542.51 2.49 2.45 2.42 2.38 2.33 glide Discharge % (relative 100.5 100.099.5 98.9 98.4 97.9 97.3 96.8 pressure to 410A) RCL g/m³ 48.5 47.5 46.645.7 44.9 44.1 43.3 42.5

TABLE 23 Example Example Example Example Example Example Example ExampleItem Unit 138 139 140 141 142 143 144 145 HFO-1132(E) mass % 56.0 58.060.0 30.0 32.0 34.0 36.0 38.0 HFO-1123 mass % 20.0 18.0 16.0 44.0 42.040.0 38.0 36.0 R1234yf mass % 24.0 24.0 24.0 26.0 26.0 26.0 26.0 26.0GWP — 2 2 2 2 2 2 2 2 COP ratio % (relative 97.7 97.9 98.1 95.3 95.595.7 95.9 96.1 to 410A) Refrigerating % (relative 91.6 91.3 91.0 93.293.1 92.9 92.7 92.5 capacity ratio to 410A) Condensation ° C. 2.28 2.222.16 2.86 2.85 2.83 2.81 2.79 glide Discharge % (relative 96.2 95.6 95.1101.3 100.8 100.4 99.9 99.4 pressure to 410A) RCL g/m³ 41.8 41.1 40.453.7 52.6 51.5 50.4 49.4

TABLE 24 Example Example Example Example Example Example Example ExampleItem Unit 146 147 148 149 150 151 152 153 HFO-1132(E) mass % 40.0 42.044.0 46.0 48.0 50.0 52.0 54.0 HFO-1123 mass % 34.0 32.0 30.0 28.0 26.024.0 22.0 20.0 R1234yf mass % 26.0 26.0 26.0 26.0 26.0 26.0 26.0 26.0GWP — 2 2 2 2 2 2 2 2 COP ratio % (relative 96.3 96.5 96.7 96.9 97.197.3 97.5 97.7 to 410A) Refrigerating % (relative 92.3 92.1 91.9 91.691.4 91.2 90.9 90.6 capacity ratio to 410A) Condensation ° C. 2.77 2.742.71 2.67 2.63 2.59 2.53 2.48 glide Discharge % (relative 99.0 98.5 97.997.4 96.9 96.4 95.8 95.3 pressure to 410A) RCL g/m³ 48.4 47.4 46.5 45.744.8 44.0 43.2 42.5

TABLE 25 Example Example Example Example Example Example Example ExampleItem Unit 154 155 156 157 158 159 160 161 HFO-1132(E) mass % 56.0 58.060.0 30.0 32.0 34.0 36.0 38.0 HFO-1123 mass % 18.0 16.0 14.0 42.0 40.038.0 36.0 34.0 R1234yf mass % 26.0 26.0 26.0 28.0 28.0 28.0 28.0 28.0GWP — 2 2 2 2 2 2 2 2 COP ratio % (relative 97.9 98.2 98.4 95.6 95.896.0 96.2 96.3 to 410A) Refrigerating % (relative 90.3 90.1 89.8 92.191.9 91.7 91.5 91.3 capacity ratio to 410A) Condensation ° C. 2.42 2.352.27 3.10 3.09 3.06 3.04 3.01 glide Discharge % (relative 94.7 94.1 93.699.7 99.3 98.8 98.4 97.9 pressure to 410A) RCL g/m³ 41.7 41.0 40.3 53.652.5 51.4 50.3 49.3

TABLE 26 Example Example Example Example Example Example Example ExampleItem Unit 162 163 164 165 166 167 168 169 HFO-1132(E) mass % 40.0 42.044.0 46.0 48.0 50.0 52.0 54.0 HFO-1123 mass % 32.0 30.0 28.0 26.0 24.022.0 20.0 18.0 R1234yf mass % 28.0 28.0 28.0 28.0 28.0 28.0 28.0 28.0GWP — 2 2 2 2 2 2 2 2 COP ratio % (relative 96.5 96.7 96.9 97.2 97.497.6 97.8 98.0 to 410A) Refrigerating % (relative 91.1 90.9 90.7 90.490.2 89.9 89.7 89.4 capacity ratio to 410A) Condensation ° C. 2.98 2.942.90 2.85 2.80 2.75 2.68 2.62 glide Discharge % (relative 97.4 96.9 96.495.9 95.4 94.9 94.3 93.8 pressure to 410A) RCL g/m³ 48.3 47.4 46.4 45.644.7 43.9 43.1 42.4

TABLE 27 Example Example Example Example Example Example Example ExampleItem Unit 170 171 172 173 174 175 176 177 HFO-1132(E) mass % 56.0 58.060.0 32.0 34.0 36.0 38.0 42.0 HFO-1123 mass % 16.0 14.0 12.0 38.0 36.034.0 32.0 28.0 R1234yf mass % 28.0 28.0 28.0 30.0 30.0 30.0 30.0 30.0GWP — 2 2 2 2 2 2 2 2 COP ratio % (relative 98.2 98.4 98.6 96.1 96.296.4 96.6 97.0 to 410A) Refrigerating % (relative 89.1 88.8 88.5 90.790.5 90.3 90.1 89.7 capacity ratio to 410A) Condensation ° C. 2.54 2.462.38 3.32 3.30 3.26 3.22 3.14 glide Discharge % (relative 93.2 92.6 92.197.7 97.3 96.8 96.4 95.4 pressure to 410A) RCL g/m³ 41.7 41.0 40.3 52.451.3 50.2 49.2 47.3

TABLE 28 Example Example Example Example Example Example Example ExampleItem Unit 178 179 180 181 182 183 184 185 HFO-1132(E) mass % 44.0 46.048.0 50.0 52.0 54.0 56.0 58.0 HFO-1123 mass % 26.0 24.0 22.0 20.0 18.016.0 14.0 12.0 R1234yf mass % 30.0 30.0 30.0 30.0 30.0 30.0 30.0 30.0GWP — 2 2 2 2 2 2 2 2 COP ratio % (relative 97.2 97.4 97.6 97.8 98.098.3 98.5 98.7 to 410A) Refrigerating % (relative 89.4 89.2 89.0 88.788.4 88.2 87.9 87.6 capacity ratio to 410A) Condensation ° C. 3.08 3.032.97 2.90 2.83 2.75 2.66 2.57 glide Discharge % (relative 94.9 94.4 93.993.3 92.8 92.3 91.7 91.1 pressure to 410A) RCL g/m³ 46.4 45.5 44.7 43.943.1 42.3 41.6 40.9

TABLE 29 Example Example Example Example Example Example Example ExampleItem Unit 186 187 188 189 190 191 192 193 HFO-1132(E) mass % 30.0 32.034.0 36.0 38.0 40.0 42.0 44.0 HFO-1123 mass % 38.0 36.0 34.0 32.0 30.028.0 26.0 24.0 R1234yf mass % 32.0 32.0 32.0 32.0 32.0 32.0 32.0 32.0GWP — 2 2 2 2 2 2 2 2 COP ratio % (relative 96.2 96.3 96.5 96.7 96.997.1 97.3 97.5 to 410A) Refrigerating % (relative 89.6 89.5 89.3 89.188.9 88.7 88.4 88.2 capacity ratio to 410A) Condensation ° C. 3.60 3.563.52 3.48 3.43 3.38 3.33 3.26 glide Discharge % (relative 96.6 96.2 95.795.3 94.8 94.3 93.9 93.4 pressure to 410A) RCL g/m³ 53.4 52.3 51.2 50.149.1 48.1 47.2 46.3

TABLE 30 Example Example Example Example Example Example Example ExampleItem Unit 194 195 196 197 198 199 200 201 HFO-1132(E) mass % 46.0 48.050.0 52.0 54.0 56.0 58.0 60.0 HFO-1123 mass % 22.0 20.0 18.0 16.0 14.012.0 10.0 8.0 R1234yf mass % 32.0 32.0 32.0 32.0 32.0 32.0 32.0 32.0 GWP— 2 2 2 2 2 2 2 2 COP ratio % (relative 97.7 97.9 98.1 98.3 98.5 98.798.9 99.2 to 410A) Refrigerating % (relative 88.0 87.7 87.5 87.2 86.986.6 86.3 86.0 capacity ratio to 410A) Condensation ° C. 3.20 3.12 3.042.96 2.87 2.77 2.66 2.55 glide Discharge % (relative 92.8 92.3 91.8 91.390.7 90.2 89.6 89.1 pressure to 410A) RCL g/m³ 45.4 44.6 43.8 43.0 42.341.5 40.8 40.2

TABLE 31 Example Example Example Example Example Example Example ExampleItem Unit 202 203 204 205 206 207 208 209 HFO-1132(E) mass % 30.0 32.034.0 36.0 38.0 40.0 42.0 44.0 HFO-1123 mass % 36.0 34.0 32.0 30.0 28.026.0 24.0 22.0 R1234yf mass % 34.0 34.0 34.0 34.0 34.0 34.0 34.0 34.0GWP — 2 2 2 2 2 2 2 2 COP ratio % (relative 96.5 96.6 96.8 97.0 97.297.4 97.6 97.8 to 410A) Refrigerating % (relative 88.4 88.2 88.0 87.887.6 87.4 87.2 87.0 capacity ratio to 410A) Condensation ° C. 3.84 3.803.75 3.70 3.64 3.58 3.51 3.43 glide Discharge % (relative 95.0 94.6 94.293.7 93.3 92.8 92.3 91.8 pressure to 410A) RCL g/m³ 53.3 52.2 51.1 50.049.0 48.0 47.1 46.2

TABLE 32 Example Example Example Example Example Example Example ExampleItem Unit 210 211 212 213 214 215 216 217 HFO-1132(E) mass % 46.0 48.050.0 52.0 54.0 30.0 32.0 34.0 HFO-1123 mass % 20.0 18.0 16.0 14.0 12.034.0 32.0 30.0 R1234yf mass % 34.0 34.0 34.0 34.0 34.0 36.0 36.0 36.0GWP — 2 2 2 2 2 2 2 2 COP ratio % (relative 98.0 98.2 98.4 98.6 98.896.8 96.9 97.1 to 410A) Refrigerating % (relative 86.7 86.5 86.2 85.985.6 87.2 87.0 86.8 capacity ratio to 410A) Condensation ° C. 3.36 3.273.18 3.08 2.97 4.08 4.03 3.97 glide Discharge % (relative 91.3 90.8 90.389.7 89.2 93.4 93.0 92.6 pressure to 410A) RCL g/m³ 45.3 44.5 43.7 42.942.2 53.2 52.1 51.0

TABLE 33 Example Example Example Example Example Example Example ExampleItem Unit 218 219 220 221 222 223 224 225 HFO-1132(E) mass % 36.0 38.040.0 42.0 44.0 46.0 30.0 32.0 HFO-1123 mass % 28.0 26.0 24.0 22.0 20.018.0 32.0 30.0 R1234yf mass % 36.0 36.0 36.0 36.0 36.0 36.0 38.0 38.0GWP — 2 2 2 2 2 2 2 2 COP ratio % (relative 97.3 97.5 97.7 97.9 98.198.3 97.1 97.2 to 410A) Refrigerating % (relative 86.6 86.4 86.2 85.985.7 85.5 85.9 85.7 capacity ratio to 410A) Condensation ° C. 3.91 3.843.76 3.68 3.60 3.50 4.32 4.25 glide Discharge % (relative 92.1 91.7 91.290.7 90.3 89.8 91.9 91.4 pressure to 410A) RCL g/m³ 49.9 48.9 47.9 47.046.1 45.3 53.1 52.0

TABLE 34 Item Unit Example 226 Example 227 HFO-1132(E) mass % 34.0 36.0HFO-1123 mass % 28.0 26.0 R1234yf mass % 38.0 38.0 GWP — 2 2 COP ratio %(relative 97.4 97.6 to 410A) Refrigerating % (relative 85.6 85.3capacity ratio to 410A) Condensation glide ° C. 4.18 4.11 Dischargepressure % (relative 91.0 90.6 to 410A) RCL g/m³ 50.9 49.8

These results indicate that under the condition that the mass % ofHFO-1132(E), HFO-1123, and R1234yf based on their sum is respectivelyrepresented by x, y, and z, when coordinates (x,y,z) in a ternarycomposition diagram in which the sum of HFO-1132(E), HFO-1123, andR1234yf is 100 mass % are within the range of a figure surrounded byline segments AA′, A′B, BD, DC′, C′C, CO, and OA that connect thefollowing 7 points:

point A (68.6, 0.0, 31.4),

point A′ (30.6, 30.0, 39.4),

point B (0.0, 58.7, 41.3),

point D (0.0, 80.4, 19.6),

point C′ (19.5, 70.5, 10.0),

point C (32.9, 67.1, 0.0), and

point O (100.0, 0.0, 0.0),

or on the above line segments (excluding the points on the line segmentCO);

the line segment AA′ is represented by coordinates (x,0.0016x²−0.9473x+57.497, −0.0016x² 0.0527x+42.503),

the line segment A′B is represented by coordinates (x,0.0029x²−1.0268x+58.7, −0.0029x²+0.0268x+41.3,

the line segment DC′ is represented by coordinates (x,0.0082x²−0.6671x+80.4, −0.0082x²−0.3329x+19.6),

the line segment C′C is represented by coordinates (x,0.0067x²−0.6034x+79.729, −0.0067x²−0.3966x+20.271), and

the line segments BD, CO, and OA are straight lines, the refrigerant hasa refrigerating capacity ratio of 85% or more relative to that of R410A,and a COP of 92.5% or more relative to that of R410A.

The point on the line segment AA′ was determined by obtaining anapproximate curve connecting point A, Example 1, and point A′ by theleast square method.

The point on the line segment A′B was determined by obtaining anapproximate curve connecting point A′, Example 3, and point B by theleast square method.

The point on the line segment DC′ was determined by obtaining anapproximate curve connecting point D, Example 6, and point C′ by theleast square method.

The point on the line segment C′C was determined by obtaining anapproximate curve connecting point C′, Example 4, and point C by theleast square method.

Likewise, the results indicate that when coordinates (x,y,z) are withinthe range of a figure surrounded by line segments AA′, A′B, BF, FT, TE,EO, and OA that connect the following 7 points:

point A (68.6, 0.0, 31.4),

point A′ (30.6, 30.0, 39.4),

point B (0.0, 58.7, 41.3),

point F (0.0, 61.8, 38.2),

point T (35.8, 44.9, 19.3),

point E (58.0, 42.0, 0.0) and

point O (100.0, 0.0, 0.0),

or on the above line segments (excluding the points on the line EO);

the line segment AA′ is represented by coordinates (x,0.0016x²−0.9473x+57.497, −0.0016x² 0.0527x+42.503),

the line segment A′B is represented by coordinates (x,0.0029x²−1.0268x+58.7, −0.0029x²+0.0268x+41.3),

the line segment FT is represented by coordinates (x,0.0078x²−0.7501x+61.8, −0.0078x²−0.2499x+38.2), and

the line segment TE is represented by coordinates (x,0.0067x²−0.7607x+63.525, −0.0067x² 0.2393x+36.475), and

the line segments BF, FO, and OA are straight lines, the refrigerant hasa refrigerating capacity ratio of 85% or more relative to that of R410A,and a COP of 95% or more relative to that of R410A.

The point on the line segment FT was determined by obtaining anapproximate curve connecting three points, i.e., points T, E′, and F, bythe least square method.

The point on the line segment TE was determined by obtaining anapproximate curve connecting three points, i.e., points E, R, and T, bythe least square method.

The results in Tables 1 to 34 clearly indicate that in a ternarycomposition diagram of the mixed refrigerant of HFO-1132(E), HFO-1123,and R1234yf in which the sum of these components is 100 mass %, a linesegment connecting a point (0.0, 100.0, 0.0) and a point (0.0, 0.0,100.0) is the base, the point (0.0, 100.0, 0.0) is on the left side, andthe point (0.0, 0.0, 100.0) is on the right side, when coordinates(x,y,z) are on or below the line segment LM connecting point L (63.1,31.9, 5.0) and point M (60.3, 6.2, 33.5), the refrigerant has an RCL of40 g/m³ or more.

The results in Tables 1 to 34 clearly indicate that in a ternarycomposition diagram of the mixed refrigerant of HFO-1132(E), HFO-1123and R1234yf in which their sum is 100 mass %, a line segment connectinga point (0.0, 100.0, 0.0) and a point (0.0, 0.0, 100.0) is the base, thepoint (0.0, 100.0, 0.0) is on the left side, and the point (0.0, 0.0,100.0) is on the right side, when coordinates (x,y,z) are on the linesegment QR connecting point Q (62.8, 29.6, 7.6) and point R (49.8, 42.3,7.9) or on the left side of the line segment, the refrigerant has atemperature glide of 1° C. or less.

The results in Tables 1 to 34 clearly indicate that in a ternarycomposition diagram of the mixed refrigerant of HFO-1132(E), HFO-1123,and R1234yf in which their sum is 100 mass %, a line segment connectinga point (0.0, 100.0, 0.0) and a point (0.0, 0.0, 100.0) is the base, thepoint (0.0, 100.0, 0.0) is on the left side, and the point (0.0, 0.0,100.0) is on the right side, when coordinates (x,y,z) are on the linesegment ST connecting point S (62.6, 28.3, 9.1) and point T (35.8, 44.9,19.3) or on the right side of the line segment, the refrigerant has adischarge pressure of 105% or less relative to that of 410A.

In these compositions, R1234yf contributes to reducing flammability, andsuppressing deterioration of polymerization etc. Therefore, thecomposition preferably contains R1234yf.

Further, the burning velocity of these mixed refrigerants whose mixedformulations were adjusted to WCF concentrations was measured accordingto the ANSI/ASHRAE Standard 34-2013. Compositions having a burningvelocity of 10 cm/s or less were determined to be classified as “Class2L (lower flammability).” A burning velocity test was performed usingthe apparatus shown in FIG. 1 in the following manner. In FIG. 1,reference numeral 901 refers to a sample cell, 902 refers to ahigh-speed camera, 903 refers to a xenon lamp, 904 refers to acollimating lens, 905 refers to a collimating lens, and 906 refers to aring filter. First, the mixed refrigerants used had a purity of 99.5% ormore, and were degassed by repeating a cycle of freezing, pumping, andthawing until no traces of air were observed on the vacuum gauge. Theburning velocity was measured by the closed method. The initialtemperature was ambient temperature. Ignition was performed bygenerating an electric spark between the electrodes in the center of asample cell. The duration of the discharge was 1.0 to 9.9 ms, and theignition energy was typically about 0.1 to 1.0 J. The spread of theflame was visualized using schlieren photographs. A cylindricalcontainer (inner diameter: 155 mm, length: 198 mm) equipped with twolight transmission acrylic windows was used as the sample cell, and axenon lamp was used as the light source. Schlieren images of the flamewere recorded by a high-speed digital video camera at a frame rate of600 fps and stored on a PC.

Each WCFF concentration was obtained by using the WCF concentration asthe initial concentration and performing a leak simulation using NISTStandard Reference Database REFLEAK Version 4.0.

Tables 35 and 36 show the results.

TABLE 35 Item Unit G H I WCF HFO-1132(E) mass % 72.0 72.0 72.0 HFO-1123mass % 28.0 9.6 0.0 R1234yf mass % 0.0 18.4 28.0 Burning velocity (WCF)cm/s 10 10 10

TABLE 36 Item Unit J P L N N′ K WCF HFO- mass % 47.1 55.8 63.1 68.6 65.061.3 1132 (E) HFO- mass % 52.9 42.0 31.9 16.3 7.7 5.4 1123 R1234yf mass% 0.0 2.2 5.0 15.1 27.3 33.3 Leak condition that Storage/ Storage/Storage/ Storage/ Storage/ Storage/ results in WCFF Shipping ShippingShipping Shipping Shipping Shipping, −40° C., −40° C., −40° C., −40° C.,−40° C., −40° C., 92% 90% 90% 66% 12% 0% release, release, release,release, release, release, liquid liquid gas gas gas gas phase phasephase phase phase phase side side side side side side WCFF HFO- mass %72.0 72.0 72.0 72.0 72.0 72.0 1132 (E) HFO- mass % 28.0 17.8 17.4 13.612.3 9.8 1123 R1234yf mass % 0.0 10.2 10.6 14.4 15.7 18.2 Burning cm/s 8or less 8 or less 8 or less 9 9 8 or less velocity (WCF) Burning cm/s 1010 10 10 10 10 velocity (WCFF)

The results in Table 35 clearly indicate that when a mixed refrigerantof HFO-1132(E), HFO-1123, and R1234yf contains HFO-1132(E) in aproportion of 72.0 mass % or less based on their sum, the refrigerantcan be determined to have a WCF lower flammability.

The results in Tables 36 clearly indicate that in a ternary compositiondiagram of a mixed refrigerant of HFO-1132(E), HFO-1123, and R1234yf inwhich their sum is 100 mass %, and a line segment connecting a point(0.0, 100.0, 0.0) and a point (0.0, 0.0, 100.0) is the base, whencoordinates (x,y,z) are on or below the line segments JP, PN, and NKconnecting the following 6 points:

point J (47.1, 52.9, 0.0),

point P (55.8, 42.0, 2.2),

point L (63.1,31.9,5.0)

point N (68.6, 16.3, 15.1)

point N′ (65.0, 7.7, 27.3) and

point K (61.3, 5.4, 33.3),

the refrigerant can be determined to have a WCF lower flammability, anda WCFF lower flammability.

In the diagram, the line segment PN is represented by coordinates (x,−0.1135x²+12.112x−280.43, 0.1135x²−13.112x+380.43), and the line segmentNK is represented by coordinates (x, 0.2421x²−29.955x+931.91,−0.2421x²+28.955x−831.91).

The point on the line segment PN was determined by obtaining anapproximate curve connecting three points, i.e., points P, L, and N, bythe least square method.

The point on the line segment NK was determined by obtaining anapproximate curve connecting three points, i.e., points N, N′, and K, bythe least square method.

(5-2) Refrigerant B

The refrigerant B according to the present disclosure is

a mixed refrigerant comprising trans-1,2-difluoroethylene (HFO-1132(E))and trifluoroethylene (HFO-1123) in a total amount of 99.5 mass % ormore based on the entire refrigerant, and the refrigerant comprising62.0 mass % to 72.0 mass % or 45.1 mass % to 47.1 mass % of HFO-1132(E)based on the entire refrigerant, or

a mixed refrigerant comprising HFO-1132(E) and HFO-1123 in a totalamount of 99.5 mass % or more based on the entire refrigerant, and therefrigerant comprising 45.1 mass % to 47.1 mass % of HFO-1132(E) basedon the entire refrigerant.

The refrigerant B according to the present disclosure has variousproperties that are desirable as an R410A-alternative refrigerant, i.e.,(1) a coefficient of performance equivalent to that of R410A, (2) arefrigerating capacity equivalent to that of R410A, (3) a sufficientlylow GWP, and (4) a lower flammability (Class 2L) according to the ASHRAEstandard.

When the refrigerant B according to the present disclosure is a mixedrefrigerant comprising 72.0 mass % or less of HFO-1132(E), it has WCFlower flammability. When the refrigerant B according to the presentdisclosure is a composition comprising 47.1% or less of HFO-1132(E), ithas WCF lower flammability and WCFF lower flammability, and isdetermined to be “Class 2L,” which is a lower flammable refrigerantaccording to the ASHRAE standard, and which is further easier to handle.

When the refrigerant B according to the present disclosure comprises62.0 mass % or more of HFO-1132(E), it becomes superior with acoefficient of performance of 95% or more relative to that of R410A, thepolymerization reaction of HFO-1132(E) and/or HFO-1123 is furthersuppressed, and the stability is further improved. When the refrigerantB according to the present disclosure comprises 45.1 mass % or more ofHFO-1132(E), it becomes superior with a coefficient of performance of93% or more relative to that of R410A, the polymerization reaction ofHFO-1132(E) and/or HFO-1123 is further suppressed, and the stability isfurther improved.

The refrigerant B according to the present disclosure may furthercomprise other additional refrigerants in addition to HFO-1132(E) andHFO-1123, as long as the above properties and effects are not impaired.In this respect, the refrigerant according to the present disclosurepreferably comprises HFO-1132(E) and HFO-1123 in a total amount of 99.75mass % or more, and more preferably 99.9 mass % or more, based on theentire refrigerant.

Such additional refrigerants are not limited, and can be selected from awide range of refrigerants. The mixed refrigerant may comprise a singleadditional refrigerant, or two or more additional refrigerants.

(Examples of Refrigerant B)

The present disclosure is described in more detail below with referenceto Examples of refrigerant B. However, the refrigerant B is not limitedto the Examples.

Mixed refrigerants were prepared by mixing HFO-1132(E) and HFO-1123 atmass % based on their sum shown in Tables 37 and 38.

The GWP of compositions each comprising a mixture of R410A(R32=50%/R125=50%) was evaluated based on the values stated in theIntergovernmental Panel on Climate Change (IPCC), fourth report. The GWPof HFO-1132(E), which was not stated therein, was assumed to be 1 fromHFO-1132a (GWP=1 or less) and HFO-1123 (GWP=0.3, described in PatentLiterature 1). The refrigerating capacity of compositions eachcomprising R410A and a mixture of HFO-1132(E) and HFO-1123 wasdetermined by performing theoretical refrigeration cycle calculationsfor the mixed refrigerants using the National Institute of Science andTechnology (NIST) and Reference Fluid Thermodynamic and TransportProperties Database (Refprop 9.0) under the following conditions.

Evaporating temperature: 5° C.

Condensation temperature: 45° C.

Superheating temperature: 5 K

Subcooling temperature: 5 K

Compressor efficiency: 70%

The composition of each mixture was defined as WCF. A leak simulationwas performed using NIST Standard Reference Data Base Refleak Version4.0 under the conditions of Equipment, Storage, Shipping, Leak, andRecharge according to the ASHRAE Standard 34-2013. The most flammablefraction was defined as WCFF.

Tables 1 and 2 show GWP, COP, and refrigerating capacity, which werecalculated based on these results. The COP and refrigerating capacityare ratios relative to R410A.

The coefficient of performance (COP) was determined by the followingformula.COP=(refrigerating capacity or heating capacity)/power consumption

For the flammability, the burning velocity was measured according to theANSI/ASHRAE Standard 34-2013. Both WCF and WCFF having a burningvelocity of 10 cm/s or less were determined to be “Class 2L (lowerflammability).” A burning velocity test was performed using theapparatus shown in FIG. 1 in the following manner. First, the mixedrefrigerants used had a purity of 99.5% or more, and were degassed byrepeating a cycle of freezing, pumping, and thawing until no traces ofair were observed on the vacuum gauge. The burning velocity was measuredby the closed method. The initial temperature was ambient temperature.Ignition was performed by generating an electric spark between theelectrodes in the center of a sample cell. The duration of the dischargewas 1.0 to 9.9 ms, and the ignition energy was typically about 0.1 to1.0 J. The spread of the flame was visualized using schlierenphotographs. A cylindrical container (inner diameter: 155 mm, length:198 mm) equipped with two light transmission acrylic windows was used asthe sample cell, and a xenon lamp was used as the light source.Schlieren images of the flame were recorded by a high-speed digitalvideo camera at a frame rate of 600 fps and stored on a PC.

TABLE 37 Comparative Comparative Example Example 2 ComparativeComparative 1 HFO- Example Example Example Example Example ExampleExample Item Unit R410A 1132E 3 1 2 3 4 5 4 HFO-1132E mass % — 100 80 7270 68 65 62 60 (WCF) HFO-1123 mass % 0 20 28 30 32 35 38 40 (WCF) GWP —2088 1 1 1 1 1 1 1 1 COP ratio % 100 99.7 97.5 96.6 96.3 96.1 95.8 95.495.2 (relative to R410A) Refrigerating % 100 98.3 101.9 103.1 103.4103.8 104.1 104.5 104.8 capacity (relative ratio to R410A) Discharge Mpa2.73 2.71 2.89 2.96 2.98 3.00 3.02 3.04 3.06 pressure Burning cm/secNon- 20 13 10 9 9 8 8 or 8 or less velocity flammable less (WCF)

TABLE 38 Comparative Comparative Comparative Example Example ExampleComparative Comparative Comparative Example 10 Item Unit Example 5Example 6 7 8 9 Example 7 Example 8 Example 9 HFO-1123 HFO-1132E mass %50 48 47.1 46.1 45.1 43 40 25 0 (WCF) HFO-1123 mass % 50 52 52.9 53.954.9 57 60 75 100 (WCF) GWP — 1 1 1 1 1 1 1 1 1 COP ratio % 94.1 93.993.8 93.7 93.6 93.4 93.1 91.9 90.6 (relative to R410A) Refrigerating %105.9 106.1 106.2 106.3 106.4 106.6 106.9 107.9 108.0 capacity (relativeratio to R410A) Discharge Mpa 3.14 3.16 3.16 3.17 3.18 3.20 3.21 3.313.39 pressure Leakage test Storage/ Storage/ Storage/ Storage/ Storage/Storage/ Storage/ Storage/ — conditions (WCFF) Shipping ShippingShipping Shipping Shipping Shipping Shipping Shipping −40° C., −40° C.,40° C., 40° C., 40° C., −40° C., −40° C., −40° C., 92% 92% 92% 92% 92%92% 92% 90% release, release, release, release, release, release,release, release, liquid liquid liquid liquid liquid liquid liquidliquid phase phase phase phase phase phase phase phase side side sideside side side side side HFO-1132E mass % 74 73 72 71 70 67 63 38 —(WCFF) HFO-1123 mass % 26 27 28 29 30 33 37 62 (WCFF) Burning cm/sec 8or 8 or 8 or 8 or 8 or 8 or 8 or 8 or 5 velocity less less less lessless less less less (WCF) Burning cm/sec 11 10.5 10.0 9.5 9.5 8.5 8 or 8or velocity less less (WCFF) ASHRAE flammability 2 2 2L 2L 2L 2L 2L 2L2L classification

The compositions each comprising 62.0 mass % to 72.0 mass % ofHFO-1132(E) based on the entire composition are stable while having alow GWP (GWP=1), and they ensure WCF lower flammability. Further,surprisingly, they can ensure performance equivalent to that of R410A.Moreover, compositions each comprising 45.1 mass % to 47.1 mass % ofHFO-1132(E) based on the entire composition are stable while having alow GWP (GWP=1), and they ensure WCFF lower flammability. Further,surprisingly, they can ensure performance equivalent to that of R410A.

(5-3) Refrigerant C

The refrigerant C according to the present disclosure is a compositioncomprising trans-1,2-difluoroethylene (HFO-1132(E)), trifluoroethylene(HFO-1123), 2,3,3,3-tetrafluoro-1-propene (R1234yf), and difluoromethane(R32), and satisfies the following requirements. The refrigerant Caccording to the present disclosure has various properties that aredesirable as an alternative refrigerant for R410A; i.e. it has acoefficient of performance and a refrigerating capacity that areequivalent to those of R410A, and a sufficiently low GWP.

Requirements

Preferable refrigerant C is as follows:

When the mass % of HFO-1132(E), HFO-1123, R1234yf, and R32 based ontheir sum is respectively represented by x, y, z, and a,

if 0<a≤11.1, coordinates (x,y,z) in a ternary composition diagram inwhich the sum of HFO-1132(E), HFO-1123, and R1234yf is (100−a) mass %are within the range of a figure surrounded by straight lines GI, IA,AB, BD′, D′C, and CG that connect the following 6 points:

point G (0.026a²−1.7478a+72.0, −0.026a²+0.7478a+28.0, 0.0),

point I (0.026a²−1.7478a+72.0, 0.0, −0.026a²+0.7478a+28.0),

point A (0.0134a²−1.9681a+68.6, 0.0, −0.0134a²+0.9681a+31.4),

point B (0.0, 0.0144a²−1.6377a+58.7, −0.0144a²+0.6377a+41.3),

point D′ (0.0, 0.0224a²+0.968a+75.4, −0.0224a²−1.968a+24.6), and

point C (−0.2304a²−0.4062a+32.9, 0.2304a²−0.5938a+67.1, 0.0),

or on the straight lines GI, AB, and D′C (excluding point G, point I,point A, point B, point D′, and point C);

if 11.1<a≤18.2, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines GI, IA,AB, BW, and WG that connect the following 5 points:

point G (0.02a²−1.6013a+71.105, −0.02a²+0.6013a+28.895, 0.0),

point I (0.02a²−1.6013a+71.105, 0.0, −0.02a²+0.6013a+28.895),

point A (0.0112a²−1.9337a+68.484, 0.0, −0.0112a²+0.9337a+31.516),

point B (0.0, 0.0075a²−1.5156a+58.199, −0.0075a²+0.5156a+41.801) and

point W (0.0, 100.0−a, 0.0),

or on the straight lines GI and AB (excluding point G, point I, point A,point B, and point W);

if 18.2<a≤26.7, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines GI, IA,AB, BW, and WG that connect the following 5 points:

point G (0.0135a²−1.4068a+69.727, −0.0135a²+0.4068a+30.273, 0.0),

point I (0.0135a²−1.4068a+69.727, 0.0, −0.0135a²+0.4068a+30.273),

point A (0.0107a²−1.9142a+68.305, 0.0, −0.0107a²+0.9142a+31.695),

point B (0.0, 0.009a²−1.6045a+59.318, −0.009a²+0.6045a+40.682) and

point W (0.0, 100.0−a, 0.0),

or on the straight lines GI and AB (excluding point G, point I, point A,point B, and point W);

if 26.7<a≤36.7, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines GI, IA,AB, BW, and WG that connect the following 5 points:

point G (0.0111a²−1.3152a+68.986, −0.0111a²+0.3152a+31.014, 0.0),

point I (0.0111a²−1.3152a+68.986, 0.0, −0.0111a²+0.3152a+31.014),

point A (0.0103a²−1.9225a+68.793, 0.0, −0.0103a²+0.9225a+31.207),

point B (0.0, 0.0046a²−1.41a+57.286, −0.0046a²+0.41a+42.714) and

point W (0.0, 100.0−a, 0.0),

or on the straight lines GI and AB (excluding point G, point I, point A,point B, and point W); and

if 36.7<a≤46.7, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines GI, IA,AB, BW, and WG that connect the following 5 points:

point G (0.0061a²−0.9918a+63.902, −0.0061a²−0.0082a+36.098, 0.0),

point I (0.0061a²−0.9918a+63.902, 0.0, −0.0061a²−0.0082a+36.098),

point A (0.0085a²−1.8102a+67.1, 0.0, −0.0085a²+0.8102a+32.9),

point B (0.0, 0.0012a²−1.1659a+52.95, −0.0012a²+0.1659a+47.05) and

point W (0.0, 100.0−a, 0.0),

or on the straight lines GI and AB (excluding point G, point I, point A,point B, and point W). When the refrigerant according to the presentdisclosure satisfies the above requirements, it has a refrigeratingcapacity ratio of 85% or more relative to that of R410A, and a COP ratioof 92.5% or more relative to that of R410A, and further ensures a WCFlower flammability.

The refrigerant C according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R1234yf based on their sumis respectively represented by x, y, and z,

if 0<a≤11.1, coordinates (x,y,z) in a ternary composition diagram inwhich the sum of HFO-1132(E), HFO-1123, and R1234yf is (100−a) mass %are within the range of a figure surrounded by straight lines JK′, K′B,BD′, D′C, and CJ that connect the following 5 points:

point J (0.0049a²−0.9645a+47.1, −0.0049a²−0.0355a+52.9, 0.0),

point K′ (0.0514a²−2.4353a+61.7, −0.0323a²+0.4122a+5.9,−0.0191a²+1.0231a+32.4),

point B (0.0, 0.0144a²−1.6377a+58.7, −0.0144a²+0.6377a+41.3),

point D′ (0.0, 0.0224a²+0.968a+75.4, −0.0224a²−1.968a+24.6), and

point C (−0.2304a²−0.4062a+32.9, 0.2304a²−0.5938a+67.1, 0.0),

or on the straight lines JK′, K′B, and D′C (excluding point J, point B,point D′, and point C);

if 11.1<a≤18.2, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines JK′, K′B,BW, and WJ that connect the following 4 points:

point J (0.0243a²−1.4161a+49.725, −0.0243a²+0.4161a+50.275, 0.0),

point K′ (0.0341a²−2.1977a+61.187, −0.0236a²+0.34a+5.636,−0.0105a²+0.8577a+33.177),

point B (0.0, 0.0075a²−1.5156a+58.199, −0.0075a²+0.5156a+41.801) and

point W (0.0, 100.0−a, 0.0),

or on the straight lines JK′ and K′B (excluding point J, point B, andpoint W);

if 18.2<a≤26.7, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines JK′, K′B,BW, and WJ that connect the following 4 points:

point J (0.0246a²−1.4476a+50.184, −0.0246a²+0.4476a+49.816, 0.0),

point K′ (0.0196a²−1.7863a+58.515, −0.0079a²−0.1136a+8.702,−0.0117a²+0.8999a+32.783),

point B (0.0, 0.009a²−1.6045a+59.318, −0.009a²+0.6045a+40.682) and

point W (0.0, 100.0−a, 0.0),

or on the straight lines JK′ and K′B (excluding point J, point B, andpoint W);

if 26.7<a≤36.7, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines JK′, K′A,AB, BW, and WJ that connect the following 5 points:

point J (0.0183a²−1.1399a+46.493, −0.0183a²+0.1399a+53.507, 0.0),

point K′ (−0.0051a²+0.0929a+25.95, 0.0, 0.0051a²−1.0929a+74.05),

point A (0.0103a²−1.9225a+68.793, 0.0, −0.0103a²+0.9225a+31.207),

point B (0.0, 0.0046a²−1.41a+57.286, −0.0046a²+0.41a+42.714) and

point W (0.0, 100.0−a, 0.0),

or on the straight lines JK′, K′A, and AB (excluding point J, point B,and point W); and

if 36.7<a≤46.7, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines JK′, K′A,AB, BW, and WJ that connect the following 5 points:

point J (−0.0134a²+1.0956a+7.13, 0.0134a²−2.0956a+92.87, 0.0),

point K′(−1.892a+29.443, 0.0, 0.892a+70.557),

point A (0.0085a²−1.8102a+67.1, 0.0, −0.0085a²+0.8102a+32.9),

point B (0.0, 0.0012a²−1.1659a+52.95, −0.0012a²+0.1659a+47.05) and

point W (0.0, 100.0−a, 0.0),

or on the straight lines JK′, K′A, and AB (excluding point J, point B,and point W). When the refrigerant according to the present disclosuresatisfies the above requirements, it has a refrigerating capacity ratioof 85% or more relative to that of R410A, and a COP ratio of 92.5% ormore relative to that of R410A. Additionally, the refrigerant has a WCFlower flammability and a WCFF lower flammability, and is classified as“Class 2L,” which is a lower flammable refrigerant according to theASHRAE standard.

When the refrigerant C according to the present disclosure furthercontains R32 in addition to HFO-1132 (E), HFO-1123, and R1234yf, therefrigerant may be a refrigerant wherein when the mass % of HFO-1132(E),HFO-1123, R1234yf, and R32 based on their sum is respectivelyrepresented by x, y, z, and a,

if 0<a≤10.0, coordinates (x,y,z) in a ternary composition diagram inwhich the sum of HFO-1132(E), HFO-1123, and R1234yf is (100−a) mass %are within the range of a figure surrounded by straight lines thatconnect the following 4 points:

point a (0.02a²−2.46a+93.4, 0, −0.02a²+2.46a+6.6),

point b′ (−0.008a²−1.38a+56, 0.018a²−0.53a+26.3, −0.01a²+1.91a+17.7),

point c (−0.016a²+1.02a+77.6, 0.016a²−1.02a+22.4, 0), and

point o (100.0−a, 0.0, 0.0) or on the straight lines oa, ab′, and b′c(excluding point o and point c);

if 10.0<a≤16.5, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines thatconnect the following 4 points:

point a (0.0244a²−2.5695a+94.056, 0, −0.0244a²+2.5695a+5.944),

point b′ (0.1161a²−1.9959a+59.749, 0.014a²−0.3399a+24.8,−0.1301a²+2.3358a+15.451),

point c (−0.0161a²+1.02a+77.6, 0.0161a²−1.02a+22.4, 0), and

point o (100.0−a, 0.0, 0.0),

or on the straight lines oa, ab′, and b′c (excluding point o and pointc); or

if 16.5<a≤21.8, coordinates (x,y,z) in the ternary composition diagramare within the range of a figure surrounded by straight lines thatconnect the following 4 points:

point a (0.0161a²−2.3535a+92.742, 0, −0.0161a²+2.3535a+7.258),

point b′ (−0.0435a²−0.0435a+50.406, 0.0304a²+1.8991a−0.0661,0.0739a²−1.8556a+49.6601),

point c (−0.0161a²+0.9959a+77.851, 0.0161a²−0.9959a+22.149, 0), and

point o (100.0−a, 0.0, 0.0),

or on the straight lines oa, ab′, and b′c (excluding point o and pointc). Note that when point b in the ternary composition diagram is definedas a point where a refrigerating capacity ratio of 95% relative to thatof R410A and a COP ratio of 95% relative to that of R410A are bothachieved, point b′ is the intersection of straight line ab and anapproximate line formed by connecting the points where the COP ratiorelative to that of R410A is 95%. When the refrigerant according to thepresent disclosure meets the above requirements, the refrigerant has arefrigerating capacity ratio of 95% or more relative to that of R410A,and a COP ratio of 95% or more relative to that of R410A.

The refrigerant C according to the present disclosure may furthercomprise other additional refrigerants in addition to HFO-1132(E),HFO-1123, R1234yf, and R32 as long as the above properties and effectsare not impaired. In this respect, the refrigerant according to thepresent disclosure preferably comprises HFO-1132(E), HFO-1123, R1234yf,and R32 in a total amount of 99.5 mass % or more, more preferably 99.75mass % or more, and still more preferably 99.9 mass % or more, based onthe entire refrigerant.

The refrigerant C according to the present disclosure may compriseHFO-1132(E), HFO-1123, R1234yf, and R32 in a total amount of 99.5 mass %or more, 99.75 mass % or more, or 99.9 mass % or more, based on theentire refrigerant.

Additional refrigerants are not particularly limited and can be widelyselected.

The mixed refrigerant may contain one additional refrigerant, or two ormore additional refrigerants.

(Examples of Refrigerant C)

The present disclosure is described in more detail below with referenceto Examples of refrigerant C. However, the refrigerant C is not limitedto the Examples.

Mixed refrigerants were prepared by mixing HFO-1132(E), HFO-1123,R1234yf, and R32 at mass % based on their sum shown in Tables 39 to 96.

The GWP of compositions each comprising a mixture of R410A(R32=50%/R125=50%) was evaluated based on the values stated in theIntergovernmental Panel on Climate Change (IPCC), fourth report. The GWPof HFO-1132(E), which was not stated therein, was assumed to be 1 fromHFO-1132a (GWP=1 or less) and HFO-1123 (GWP=0.3, described in PatentLiterature 1). The refrigerating capacity of compositions eachcomprising R410A and a mixture of HFO-1132(E) and HFO-1123 wasdetermined by performing theoretical refrigeration cycle calculationsfor the mixed refrigerants using the National Institute of Science andTechnology (NIST) and Reference Fluid Thermodynamic and TransportProperties Database (Refprop 9.0) under the following conditions.

For each of these mixed refrigerants, the COP ratio and therefrigerating capacity ratio relative to those of R410 were obtained.Calculation was conducted under the following conditions.

Evaporating temperature: 5° C.

Condensation temperature: 45° C.

Superheating temperature: 5 K

Subcooling temperature: 5 K

Compressor efficiency: 70%

Tables 39 to 96 show the resulting values together with the GWP of eachmixed refrigerant. The COP and refrigerating capacity are ratiosrelative to R410A.

The coefficient of performance (COP) was determined by the followingformula.COP=(refrigerating capacity or heating capacity)/power consumption

TABLE 39 Comp. Comp. Comp. Comp. Comp. Comp. Comp. Ex. Comp. Ex. 2 Ex. 3Ex. 4 Ex. 5 Ex. 6 Ex. 7 Ex. 8 1 Item Unit Ex. 1 A B C D′ G I J K′HFO-1132(E) Mass % R410A 68.6 0.0 32.9 0.0 72.0 72.0 47.1 61.7 HFO-1123Mass % 0.0 58.7 67.1 75.4 28.0 0.0 52.9 5.9 R1234yf Mass % 31.4 41.3 0.024.6 0.0 28.0 0.0 32.4 R32 Mass % 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 GWP —2088 2 2 1 2 1 2 1 2 % (relative COP ratio to R410A) 100 100.0 95.5 92.593.1 96.6 99.9 93.8 99.4 Refrigerating % (relative capacity ratio toR410A) 100 85.0 85.0 107.4 95.0 103.1 86.6 106.2 85.5

TABLE 40 Comp. Comp. Comp. Comp. Comp. Comp. Comp. Ex. Ex. 9 Ex. 10 Ex.11 Ex. 12 Ex. 13 Ex. 14 Ex. 15 2 Item Unit A B C D′ G I J K′ HFO-1132(E)Mass % 55.3 0.0 18.4 0.0 60.9 60.9 40.5 47.0 HFO-1123 Mass % 0.0 47.874.5 83.4 32.0 0.0 52.4 7.2 R1234yf Mass % 37.6 45.1 0.0 9.5 0.0 32.00.0 38.7 R32 Mass % 7.1 7.1 7.1 7.1 7.1 7.1 7.1 7.1 GWP — 50 50 49 49 4950 49 50 COP ratio % (relative 99.8 96.9 92.5 92.5 95.9 99.6 94.0 99.2to R410A) Refrigerating % (relative 85.0 85.0 110.5 106.0 106.5 87.7108.9 85.5 capacity ratio to R410A)

TABLE 41 Comp. Comp. Comp. Comp. Comp. Comp. Ex. Ex. 16 Ex. 17 Ex. 18Ex.19 Ex. 20 Ex. 21 3 Item Unit A B C = D′ G I J K′ HFO-1132(E) Mass %48.4 0.0 0.0 55.8 55.8 37.0 41.0 HFO-1123 Mass % 0.0 42.3 88.9 33.1 0.051.9 6.5 R1234yf Mass % 40.5 46.6 0.0 0.0 33.1 0.0 41.4 R32 Mass % 11.111.1 11.1 11.1 11.1 11.1 11.1 GWP — 77 77 76 76 77 76 77 COP ratio %(relative 99.8 97.6 92.5 95.8 99.5 94.2 99.3 to R410A) Refrigerating %(relative 85.0 85.0 112.0 108.0 88.6 110.2 85.4 capacity ratio to R410A)

TABLE 42 Comp. Comp. Comp. Comp. Comp. Ex. Ex. 22 Ex. 23 Ex. 24 Ex. 25Ex. 26 4 Item Unit A B G I J K′ HFO-1132(E) Mass % 42.8 0.0 52.1 52.134.3 36.5 HFO-1123 Mass % 0.0 37.8 33.4 0.0 51.2 5.6 R1234yf Mass % 42.747.7 0.0 33.4 0.0 43.4 R32 Mass % 14.5 14.5 14.5 14.5 14.5 14.5 GWP —100 100 99 100 99 100 COP ratio % (relative 99.9 98.1 95.8 99.5 94.499.5 to R410A) Refrigerating % (relative 85.0 85.0 109.1 89.6 111.1 85.3capacity ratio to R410A)

TABLE 43 Comp. Comp. Comp. Comp. Comp. Ex. Ex. 27 Ex. 28 Ex. 29 Ex. 30Ex. 31 5 Item Unit A B G I J K′ HFO-1132(E) Mass % 37.0 0.0 48.6 48.632.0 32.5 HFO-1123 Mass % 0.0 33.1 33.2 0.0 49.8 4.0 R1234yf Mass % 44.848.7 0.0 33.2 0.0 45.3 R32 Mass % 18.2 18.2 18.2 18.2 18.2 18.2 GWP —125 125 124 125 124 125 COP ratio % (relative 100.0 98.6 95.9 99.4 94.799.8 to R410A) Refrigerating % (relative 85.0 85.0 110.1 90.8 111.9 85.2capacity ratio to R410A)

TABLE 44 Comp. Comp. Comp. Comp. Comp. Ex. Ex. 32 Ex. 33 Ex. 34 Ex. 35Ex. 36 6 Item Unit A B G I J K′ HFO-1132(E) Mass % 31.5 0.0 45.4 45.430.3 28.8 HFO-1123 Mass % 0.0 28.5 32.7 0.0 47.8 2.4 R1234yf Mass % 46.649.6 0.0 32.7 0.0 46.9 R32 Mass % 21.9 21.9 21.9 21.9 21.9 21.9 GWP —150 150 149 150 149 150 COP ratio % (relative 100.2 99.1 96.0 99.4 95.1100.0 to R410A) Refrigerating % (relative 85.0 85.0 111.0 92.1 112.685.1 capacity ratio to R410A)

TABLE 45 Comp. Comp. Comp. Comp. Comp. Comp. Ex. 37 Ex. 38 Ex. 39 Ex. 40Ex. 41 Ex. 42 Item Unit A B G I J K′ HFO-1132(E) Mass % 24.8 0.0 41.841.8 29.1 24.8 HFO-1123 Mass % 0.0 22.9 31.5 0.0 44.2 0.0 R1234yf Mass %48.5 50.4 0.0 31.5 0.0 48.5 R32 Mass % 26.7 26.7 26.7 26.7 26.7 26.7 GWP— 182 182 181 182 181 182 COP ratio % (relative 100.4 99.8 96.3 99.495.6 100.4 to R410A) Refrigerating % (relative 85.0 85.0 111.9 93.8113.2 85.0 capacity ratio to R410A)

TABLE 46 Comp. Comp. Comp. Comp. Comp. Comp. Ex. 43 Ex.44 Ex. 45 Ex. 46Ex. 47 Ex. 48 Item Unit A B G I J K′ HFO-1132(E) Mass % 21.3 0.0 40.040.0 28.8 24.3 HFO-1123 Mass % 0.0 19.9 30.7 0.0 41.9 0.0 R1234yf Mass %49.4 50.8 0.0 30.7 0.0 46.4 R32 Mass % 29.3 29.3 29.3 29.3 29.3 29.3 GWP— 200 200 198 199 198 200 COP ratio % (relative 100.6 100.1 96.6 99.596.1 100.4 to R410A) Refrigerating % (relative 85.0 85.0 112.4 94.8113.6 86.7 capacity ratio to R410A)

TABLE 47 Comp. Comp. Comp. Comp. Comp. Comp. Ex. 49 Ex. 50 Ex. 51 Ex. 52Ex. 53 Ex. 54 Item Unit A B G I J K′ HFO-1132(E) Mass % 12.1 0.0 35.735.7 29.3 22.5 HFO-1123 Mass % 0.0 11.7 27.6 0.0 34.0 0.0 R1234yf Mass %51.2 51.6 0.0 27.6 0.0 40.8 R32 Mass % 36.7 36.7 36.7 36.7 36.7 36.7 GWP— 250 250 248 249 248 250 COP ratio % (relative 101.2 101.0 96.4 99.697.0 100.4 to R410A) Refrigerating % (relative 85.0 85.0 113.2 97.6113.9 90.9 capacity ratio to R410A)

TABLE 48 Comp. Comp. Comp. Comp. Comp. Comp. Ex. 55 Ex. 56 Ex. 57 Ex. 58Ex. 59 Ex. 60 Item Unit A B G I J K′ HFO-1132(E) Mass % 3.8 0.0 32.032.0 29.4 21.1 HFO-1123 Mass % 0.0 3.9 23.9 0.0 26.5 0.0 R1234yf Mass %52.1 52.0 0.0 23.9 0.0 34.8 R32 Mass % 44.1 44.1 44.1 44.1 44.1 44.1 GWP— 300 300 298 299 298 299 COP ratio % (relative 101.8 101.8 97.9 99.897.8 100.5 to R410A) Refrigerating % (relative 85.0 85.0 113.7 100.4113.9 94.9 capacity ratio to R410A)

TABLE 49 Comp. Comp. Comp. Comp. Comp. Ex. 61 Ex. 62 Ex. 63 Ex. 64 Ex.65 Item Unit A = B G I J K′ HFO- Mass % 0.0 30.4 30.4 28.9 20.4 1132(E)HFO-1123 Mass % 0.0 21.8 0.0 23.3 0.0 R1234yf Mass % 52.2 0.0 21.8 0.031.8 R32 Mass % 47.8 47.8 47.8 47.8 47.8 GWP — 325 323 324 323 324 COPratio % 102.1 98.2 100.0 98.2 100.6 (relative to R410A) Refrigerating %85.0 113.8 101.8 113.9 96.8 capacity (relative ratio to R410A)

TABLE 50 Comp. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit Ex. 66 7 8 9 10 1112 13 HFO-1132(E) Mass % 5.0 10.0 15.0 20.0 25.0 30.0 35.0 40.0 HFO-1123Mass % 82.9 77.9 72.9 67.9 62.9 57.9 52.9 47.9 R1234yf Mass % 5.0 5.05.0 5.0 5.0 5.0 5.0 5.0 R32 Mass % 7.1 7.1 7.1 7.1 7.1 7.1 7.1 7.1 GWP —49 49 49 49 49 49 49 49 COP ratio % (relative 92.4 92.6 92.8 93.1 93.493.7 94.1 94.5 to R410A) Refrigerating % (relative 108.4 108.3 108.2107.9 107.6 107.2 106.8 106.3 capacity ratio to R410A)

TABLE 51 Ex. Ex. Ex. Ex. Comp. Ex. Ex. Ex. Item Unit 14 15 16 17 Ex. 6718 19 20 HFO-1132(E) Mass % 45.0 50.0 55.0 60.0 65.0 10.0 15.0 20.0HFO-1123 Mass % 42.9 37.9 32.9 27.9 22.9 72.9 67.9 62.9 R1234yf Mass %5.0 5.0 5.0 5.0 5.0 10.0 10.0 10.0 R32 Mass % 7.1 7.1 7.1 7.1 7.1 7.17.1 7.1 GWP — 49 49 49 49 49 49 49 49 COP ratio % (relative 95.0 95.495.9 96.4 96.9 93.0 93.3 93.6 to R410A) Refrigerating % (relative 105.8105.2 104.5 103.9 103.1 105.7 105.5 105.2 capacity ratio to R410A)

TABLE 52 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 21 22 23 24 25 26 2728 HFO-1132(E) Mass % 25.0 30.0 35.0 40.0 45.0 50.0 55.0 60.0 HFO-1123Mass % 57.9 52.9 47.9 42.9 37.9 32.9 27.9 22.9 R1234yf Mass % 10.0 10.010.0 10.0 10.0 10.0 10.0 10.0 R32 Mass % 7.1 7.1 7.1 7.1 7.1 7.1 7.1 7.1GWP — 49 49 49 49 49 49 49 49 COP ratio % (relative 93.9 94.2 94.6 95.095.5 96.0 96.4 96.9 to R410A) Refrigerating % (relative 104.9 104.5104.1 103.6 103.0 102.4 101.7 101.0 capacity ratio to R410A)

TABLE 53 Comp. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit Ex. 68 29 30 31 3233 34 35 HFO-1132(E) Mass % 65.0 10.0 15.0 20.0 25.0 30.0 35.0 40.0HFO-1123 Mass % 17.9 67.9 62.9 57.9 52.9 47.9 42.9 37.9 R1234yf Mass %10.0 15.0 15.0 15.0 15.0 15.0 15.0 15.0 R32 Mass % 7.1 7.1 7.1 7.1 7.17.1 7.1 7.1 GWP — 49 49 49 49 49 49 49 49 COP ratio % (relative 97.493.5 93.8 94.1 94.4 94.8 95.2 95.6 to R410A) Refrigerating % (relative100.3 102.9 102.7 102.5 102.1 101.7 101.2 100.7 capacity ratio to R410A)

TABLE 54 Ex. Ex. Ex. Ex. Comp. Ex. Ex. Ex. Item Unit 36 37 38 39 Ex. 6940 41 42 HFO-1132(E) Mass % 45.0 50.0 55.0 60.0 65.0 10.0 15.0 20.0HFO-1123 Mass % 32.9 27.9 22.9 17.9 12.9 62.9 57.9 52.9 R1234yf Mass %15.0 15.0 15.0 15.0 15.0 20.0 20.0 20.0 R32 Mass % 7.1 7.1 7.1 7.1 7.17.1 7.1 7.1 GWP — 49 49 49 49 49 49 49 49 COP ratio % (relative 96.096.5 97.0 97.5 98.0 94.0 94.3 94.6 to R410A) Refrigerating % (relative100.1 99.5 98.9 98.1 97.4 100.1 99.9 99.6 capacity ratio to R410A)

TABLE 55 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 43 44 45 46 47 48 4950 HFO-1132(E) Mass % 25.0 30.0 35.0 40.0 45.0 50.0 55.0 60.0 HFO-1123Mass % 47.9 42.9 37.9 32.9 27.9 22.9 17.9 12.9 R1234yf Mass % 20.0 20.020.0 20.0 20.0 20.0 20.0 20.0 R32 Mass % 7.1 7.1 7.1 7.1 7.1 7.1 7.1 7.1GWP — 49 49 49 49 49 49 49 49 COP ratio % (relative 95.0 95.3 95.7 96.296.6 97.1 97.6 98.1 to R410A) Refrigerating % (relative 99.2 98.8 98.397.8 97.2 96.6 95.9 95.2 capacity ratio to R410A)

TABLE 56 Comp. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit Ex. 70 51 52 53 5455 56 57 HFO-1132(E) Mass % 65.0 10.0 15.0 20.0 25.0 30.0 35.0 40.0HFO-1123 Mass % 7.9 57.9 52.9 47.9 42.9 37.9 32.9 27.9 R1234yf Mass %20.0 25.0 25.0 25.0 25.0 25.0 25.0 25.0 R32 Mass % 7.1 7.1 7.1 7.1 7.17.1 7.1 7.1 GWP — 49 50 50 50 50 50 50 50 COP ratio % (relative 98.694.6 94.9 95.2 95.5 95.9 96.3 96.8 to R410A) Refrigerating % (relative94.4 97.1 96.9 96.7 96.3 95.9 95.4 94.8 capacity ratio to R410A)

TABLE 57 Ex. Ex. Ex. Ex. Comp. Ex. Ex. Ex. Item Unit 58 59 60 61 Ex. 7162 63 64 HFO-1132(E) Mass % 45.0 50.0 55.0 60.0 65.0 10.0 15.0 20.0HFO-1123 Mass % 7.1 7.1 7.1 7.1 7.1 7.1 7.1 7.1 R1234yf Mass % 25.0 25.025.0 25.0 25.0 30.0 30.0 30.0 R32 Mass % 7.1 7.1 7.1 7.1 7.1 7.1 7.1 7.1GWP — 50 50 50 50 50 50 50 50 COP ratio % (relative 97.2 97.7 98.2 98.799.2 95.2 95.5 95.8 to R410A) Refrigerating % (relative 94.2 93.6 92.992.2 91.4 94.2 93.9 93.7 capacity ratio to R410A)

TABLE 58 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 65 66 67 68 69 70 7172 HFO-1132(E) Mass % 25.0 30.0 35.0 40.0 45.0 50.0 55.0 60.0 HFO-1123Mass % 37.9 32.9 27.9 22.9 17.9 12.9 7.9 2.9 R1234yf Mass % 30.0 30.030.0 30.0 30.0 30.0 30.0 30.0 R32 Mass % 7.1 7.1 7.1 7.1 7.1 7.1 7.1 7.1GWP — 50 50 50 50 50 50 50 50 COP ratio % (relative 96.2 96.6 97.0 97.497.9 98.3 98.8 99.3 to R410A) Refrigerating % (relative 93.3 92.9 92.491.8 91.2 90.5 89.8 89.1 capacity ratio to R410A)

TABLE 59 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 73 74 75 76 77 78 7980 HFO-1132(E) Mass % 10.0 15.0 20.0 25.0 30.0 35.0 40.0 45.0 HFO-1123Mass % 47.9 42.9 37.9 32.9 27.9 22.9 17.9 12.9 R1234yf Mass % 35.0 35.035.0 35.0 35.0 35.0 35.0 35.0 R32 Mass % 7.1 7.1 7.1 7.1 7.1 7.1 7.1 7.1GWP — 50 50 50 50 50 50 50 50 COP ratio % (relative 95.9 96.2 96.5 96.997.2 97.7 98.1 98.5 to R410A) Refrigerating % (relative 91.1 90.9 90.690.2 89.8 89.3 88.7 88.1 capacity ratio to R410A)

TABLE 60 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 81 82 83 84 85 86 8788 HFO-1132(E) Mass % 50.0 55.0 10.0 15.0 20.0 25.0 30.0 35.0 HFO-1123Mass % 7.9 2.9 42.9 37.9 32.9 27.9 22.9 17.9 R1234yf Mass % 35.0 35.040.0 40.0 40.0 40.0 40.0 40.0 R32 Mass % 7.1 7.1 7.1 7.1 7.1 7.1 7.1 7.1GWP — 50 50 50 50 50 50 50 50 COP ratio % (relative 99.0 99.4 96.6 96.997.2 97.6 98.0 98.4 to R410A) Refrigerating % (relative 87.4 86.7 88.087.8 87.5 87.1 86.6 86.1 capacity ratio to R410A)

TABLE 61 Comp. Comp. Comp. Comp. Comp. Comp. Comp. Comp. Item Unit Ex.72 Ex. 73 Ex. 74 Ex. 75 Ex. 76 Ex. 77 Ex. 78 Ex. 79 HFO-1132(E) Mass %40.0 45.0 50.0 10.0 15.0 20.0 25.0 30.0 HFO-1123 Mass % 12.9 7.9 2.937.9 32.9 27.9 22.9 17.9 R1234yf Mass % 40.0 40.0 40.0 45.0 45.0 45.045.0 45.0 R32 Mass % 7.1 7.1 7.1 7.1 7.1 7.1 7.1 7.1 GWP — 50 50 50 5050 50 50 50 COP ratio % (relative 98.8 99.2 99.6 97.4 97.7 98.0 98.398.7 to R410A) Refrigerating % (relative 85.5 84.9 84.2 84.9 84.6 84.383.9 83.5 capacity ratio to R410A)

TABLE 62 Comp. Comp. Comp. Item Unit Ex. 80 Ex. 81 Ex. 82 HFO-1132(E)Mass % 35.0 40.0 45.0 HFO-1123 Mass % 12.9 7.9 2.9 R1234yf Mass % 45.045.0 45.0 R32 Mass % 7.1 7.1 7.1 GWP — 50 50 50 COP ratio % (relative99.1 99.5 99.9 to R410A) Refrigerating % (relative 82.9 82.3 81.7capacity ratio to R410A)

TABLE 63 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 89 90 91 92 93 94 9596 HFO-1132(E) Mass % 10.0 15.0 20.0 25.0 30.0 35.0 40.0 45.0 HFO-1123Mass % 70.5 65.5 60.5 55.5 50.5 45.5 40.5 35.5 R1234yf Mass % 5.0 5.05.0 5.0 5.0 5.0 5.0 5.0 R32 Mass % 14.5 14.5 14.5 14.5 14.5 14.5 14.514.5 GWP — 99 99 99 99 99 99 99 99 COP ratio % (relative 93.7 93.9 94.194.4 94.7 95.0 95.4 95.8 to R410A) Refrigerating % (relative 110.2 110.0109.7 109.3 108.9 108.4 107.9 107.3 capacity ratio to R410A)

TABLE 64 Ex. Comp. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 97 Ex. 83 98 99 100101 102 103 HFO-1132(E) Mass % 50.0 55.0 10.0 15.0 20.0 25.0 30.0 35.0HFO-1123 Mass % 30.5 25.5 65.5 60.5 55.5 50.5 45.5 40.5 R1234yf Mass %5.0 5.0 10.0 10.0 10.0 10.0 10.0 10.0 R32 Mass % 14.5 14.5 14.5 14.514.5 14.5 14.5 14.5 GWP — 99 99 99 99 99 99 99 99 COP ratio % (relative96.2 96.6 94.2 94.4 94.6 94.9 95.2 95.5 to R410A) Refrigerating %(relative 106.6 106.0 107.5 107.3 107.0 106.6 106.1 105.6 capacity ratioto R410A)

TABLE 65 Ex. Ex. Ex. Comp. Ex. Ex. Ex. Ex. Item Unit 104 105 106 Ex. 84107 108 109 110 HFO-1132(E) Mass % 40.0 45.0 50.0 55.0 10.0 15.0 20.025.0 HFO-1123 Mass % 35.5 30.5 25.5 20.5 60.5 55.5 50.5 45.5 R1234yfMass % 10.0 10.0 10.0 10.0 15.0 15.0 15.0 15.0 R32 Mass % 14.5 14.5 14.514.5 14.5 14.5 14.5 14.5 GWP — 99 99 99 99 99 99 99 99 COP ratio %(relative 95.9 96.3 96.7 97.1 94.6 94.8 95.1 95.4 to R410A)Refrigerating % (relative 105.1 104.5 103.8 103.1 104.7 104.5 104.1103.7 capacity ratio to R410A)

TABLE 66 Ex. Ex. Ex. Ex. Ex. Comp. Ex. Ex. Item Unit 111 112 113 114 115Ex. 85 116 117 HFO-1132(E) Mass % 30.0 35.0 40.0 45.0 50.0 55.0 10.015.0 HFO-1123 Mass % 40.5 35.5 30.5 25.5 20.5 15.5 55.5 50.5 R1234yfMass % 15.0 15.0 15.0 15.0 15.0 15.0 20.0 20.0 R32 Mass % 14.5 14.5 14.514.5 14.5 14.5 14.5 14.5 GWP — 99 99 99 99 99 99 99 99 COP ratio %(relative 95.7 96.0 96.4 96.8 97.2 97.6 95.1 95.3 to R410A)Refrigerating % (relative 103.3 102.8 102.2 101.6 101.0 100.3 101.8101.6 capacity ratio to R410A)

TABLE 67 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Comp. Item Unit 118 119 120 121 122123 124 Ex. 86 HFO-1132(E) Mass % 20.0 25.0 30.0 35.0 40.0 45.0 50.055.0 HFO-1123 Mass % 45.5 40.5 35.5 30.5 25.5 20.5 15.5 10.5 R1234yfMass % 20.0 20.0 20.0 20.0 20.0 20.0 20.0 20.0 R32 Mass % 14.5 14.5 14.514.5 14.5 14.5 14.5 14.5 GWP — 99 99 99 99 99 99 99 99 COP ratio %(relative 95.6 95.9 96.2 96.5 96.9 97.3 97.7 98.2 to R410A)Refrigerating % (relative 101.2 100.8 100.4 99.9 99.3 98.7 98.0 97.3capacity ratio to R410A)

TABLE 68 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 125 126 127 128 129130 131 132 HFO-1132(E) Mass % 10.0 15.0 20.0 25.0 30.0 35.0 40.0 45.0HFO-1123 Mass % 50.5 45.5 40.5 35.5 30.5 25.5 20.5 15.5 R1234yf Mass %25.0 25.0 25.0 25.0 25.0 25.0 25.0 25.0 R32 Mass % 14.5 14.5 14.5 14.514.5 14.5 14.5 14.5 GWP — 99 99 99 99 99 99 99 99 COP ratio % (relative95.6 95.9 96.1 96.4 96.7 97.1 97.5 97.9 to R410A) Refrigerating %(relative to 98.9 98.6 98.3 97.9 97.4 96.9 96.3 95.7 capacity ratioR410A)

TABLE 69 Ex. Comp. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 133 Ex. 87 134 135136 137 138 139 HFO-1132(E) Mass % 50.0 55.0 10.0 15.0 20.0 25.0 30.035.0 HFO-1123 Mass % 10.5 5.5 45.5 40.5 35.5 30.5 25.5 20.5 R1234yf Mass% 25.0 25.0 30.0 30.0 30.0 30.0 30.0 30.0 R32 Mass % 14.5 14.5 14.5 14.514.5 14.5 14.5 14.5 GWP — 99 99 100 100 100 100 100 100 COP ratio %(relative 98.3 98.7 96.2 96.4 96.7 97.0 97.3 97.7 to R410A)Refrigerating % (relative 95.0 94.3 95.8 95.6 95.2 94.8 94.4 93.8capacity ratio to R410A)

TABLE 70 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 140 141 142 143 144145 146 147 HFO-1132(E) Mass % 40.0 45.0 50.0 10.0 15.0 20.0 25.0 30.0HFO-1123 Mass % 15.5 10.5 5.5 40.5 35.5 30.5 25.5 20.5 R1234yf Mass %30.0 30.0 30.0 35.0 35.0 35.0 35.0 35.0 R32 Mass % 14.5 14.5 14.5 14.514.5 14.5 14.5 14.5 GWP — 100 100 100 100 100 100 100 100 COP ratio %(relative 98.1 98.5 98.9 96.8 97.0 97.3 97.6 97.9 to R410A)Refrigerating % (relative 93.3 92.6 92.0 92.8 92.5 92.2 91.8 91.3capacity ratio to R410A)

TABLE 71 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 148 149 150 151 152153 154 155 HFO-1132(E) Mass % 35.0 40.0 45.0 10.0 15.0 20.0 25.0 30.0HFO-1123 Mass % 15.5 10.5 5.5 35.5 30.5 25.5 20.5 15.5 R1234yf Mass %35.0 35.0 35.0 40.0 40.0 40.0 40.0 40.0 R32 Mass % 14.5 14.5 14.5 14.514.5 14.5 14.5 14.5 GWP — 100 100 100 100 100 100 100 100 COP ratio %(relative 98.3 98.7 99.1 97.4 97.7 98.0 98.3 98.6 to R410A)Refrigerating % (relative 90.8 90.2 89.6 89.6 89.4 89.0 88.6 88.2capacity ratio to R410A)

TABLE 72 Ex. Ex. Ex. Ex. Ex. Comp. Comp. Comp. Item Unit 156 157 158 159160 Ex. 88 Ex. 89 Ex. 90 HFO-1132(E) Mass % 35.0 40.0 10.0 15.0 20.025.0 30.0 35.0 HFO-1123 Mass % 10.5 5.5 30.5 25.5 20.5 15.5 10.5 5.5R1234yf Mass % 40.0 40.0 45.0 45.0 45.0 45.0 45.0 45.0 R32 Mass % 14.514.5 14.5 14.5 14.5 14.5 14.5 14.5 GWP — 100 100 100 100 100 100 100 100COP ratio % (relative 98.9 99.3 98.1 98.4 98.7 98.9 99.3 99.6 to R410A)Refrigerating % (relative 87.6 87.1 86.5 86.2 85.9 85.5 85.0 84.5capacity ratio to R410A)

TABLE 73 Comp. Comp. Comp. Comp. Comp. Item Unit Ex. 91 Ex. 92 Ex. 93Ex. 94 Ex. 95 HFO- Mass % 10.0 15.0 20.0 25.0 30.0 1132(E) HFO-1123 Mass% 25.5 20.5 15.5 10.5 5.5 R1234yf Mass % 50.0 50.0 50.0 50.0 50.0 R32Mass % 14.5 14.5 14.5 14.5 14.5 GWP — 100 100 100 100 100 COP ratio %98.9 99.1 99.4 99.7 100.0 (relative to R410A) Refrigerating % 83.3 83.082.7 82.2 81.8 capacity (relative ratio to R410A)

TABLE 74 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 161 162 163 164 165166 167 168 HFO-1132(E) Mass % 10.0 15.0 20.0 25.0 30.0 35.0 40.0 45.0HFO-1123 Mass % 63.1 58.1 53.1 48.1 43.1 38.1 33.1 28.1 R1234yf Mass %5.0 5.0 5.0 5.0 5.0 5.0 5.0 5.0 R32 Mass % 21.9 21.9 21.9 21.9 21.9 21.921.9 21.9 GWP — 149 149 149 149 149 149 149 149 COP ratio % (relative94.8 95.0 95.2 95.4 95.7 95.9 96.2 96.6 to R410A) Refrigerating %(relative 111.5 111.2 110.9 110.5 110.0 109.5 108.9 108.3 capacity ratioto R410A)

TABLE 75 Comp. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit Ex. 96 169 170 171172 173 174 175 HFO-1132(E) Mass % 50.0 10.0 15.0 20.0 25.0 30.0 35.040.0 HFO-1123 Mass % 23.1 58.1 53.1 48.1 43.1 38.1 33.1 28.1 R1234yfMass % 5.0 10.0 10.0 10.0 10.0 10.0 10.0 10.0 R32 Mass % 21.9 21.9 21.921.9 21.9 21.9 21.9 21.9 GWP — 149 149 149 149 149 149 149 149 COP ratio% (relative 96.9 95.3 95.4 95.6 95.8 96.1 96.4 96.7 to R410A)Refrigerating % (relative 107.7 108.7 108.5 108.1 107.7 107.2 106.7106.1 capacity ratio to R410A)

TABLE 76 Ex. Comp. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 176 Ex. 97 177 178179 180 181 182 HFO-1132(E) Mass % 45.0 50.0 10.0 15.0 20.0 25.0 30.035.0 HFO-1123 Mass % 23.1 18.1 53.1 48.1 43.1 38.1 33.1 28.1 R1234yfMass % 10.0 10.0 15.0 15.0 15.0 15.0 15.0 15.0 R32 Mass % 21.9 21.9 21.921.9 21.9 21.9 21.9 21.9 GWP — 149 149 149 149 149 149 149 149 COP ratio% (relative 97.0 97.4 95.7 95.9 96.1 96.3 96.6 96.9 to R410A)Refrigerating % (relative 105.5 104.9 105.9 105.6 105.3 104.8 104.4103.8 capacity ratio to R410A)

TABLE 77 Ex. Ex. Comp. Ex. Ex. Ex. Ex. Ex. Item Unit 183 184 Ex. 98 185186 187 188 189 HFO-1132(E) Mass % 40.0 45.0 50.0 10.0 15.0 20.0 25.030.0 HFO-1123 Mass % 23.1 18.1 13.1 48.1 43.1 38.1 33.1 28.1 R1234yfMass % 15.0 15.0 15.0 20.0 20.0 20.0 20.0 20.0 R32 Mass % 21.9 21.9 21.921.9 21.9 21.9 21.9 21.9 GWP — 149 149 149 149 149 149 149 149 COP ratio% (relative 97.2 97.5 97.9 96.1 96.3 96.5 96.8 97.1 to R410A)Refrigerating % (relative 103.3 102.6 102.0 103.0 102.7 102.3 101.9101.4 capacity ratio to R410A)

TABLE 78 Ex. Ex. Ex. Comp. Ex. Ex. Ex. Ex. Item Unit 190 191 192 Ex. 99193 194 195 196 HFO-1132(E) Mass % 35.0 40.0 45.0 50.0 10.0 15.0 20.025.0 HFO-1123 Mass % 23.1 18.1 13.1 8.1 43.1 38.1 33.1 28.1 R1234yf Mass% 20.0 20.0 20.0 20.0 25.0 25.0 25.0 25.0 R32 Mass % 21.9 21.9 21.9 21.921.9 21.9 21.9 21.9 GWP — 149 149 149 149 149 149 149 149 COP ratio %(relative 97.4 97.7 98.0 98.4 96.6 96.8 97.0 97.3 to R410A)Refrigerating % (relative 100.9 100.3 99.7 99.1 100.0 99.7 99.4 98.9capacity ratio to R410A)

TABLE 79 Ex. Ex. Ex. Ex. Comp. Ex. Ex. Ex. Item Unit 197 198 199 200 Ex.100 201 202 203 HFO-1132(E) Mass % 30.0 35.0 40.0 45.0 50.0 10.0 15.020.0 HFO-1123 Mass % 23.1 18.1 13.1 8.1 3.1 38.1 33.1 28.1 R1234yf Mass% 25.0 25.0 25.0 25.0 25.0 30.0 30.0 30.0 R32 Mass % 21.9 21.9 21.9 21.921.9 21.9 21.9 21.9 GWP — 149 149 149 149 149 150 150 150 COP ratio %(relative 97.6 97.9 98.2 98.5 98.9 97.1 97.3 97.6 to R410A)Refrigerating % (relative 98.5 97.9 97.4 96.8 96.1 97.0 96.7 96.3capacity ratio to R410A)

TABLE 80 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 204 205 206 207 208209 210 211 HFO-1132(E) Mass % 25.0 30.0 35.0 40.0 45.0 10.0 15.0 20.0HFO-1123 Mass % 23.1 18.1 13.1 8.1 3.1 33.1 28.1 23.1 R1234yf Mass %30.0 30.0 30.0 30.0 30.0 35.0 35.0 35.0 R32 Mass % 21.9 21.9 21.9 21.921.9 21.9 21.9 21.9 GWP — 150 150 150 150 150 150 150 150 COP ratio %(relative 97.8 98.1 98.4 98.7 99.1 97.7 97.9 98.1 to R410A)Refrigerating % (relative 95.9 95.4 94.9 94.4 93.8 93.9 93.6 93.3capacity ratio to R410A)

TABLE 81 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 212 213 214 215 216217 218 219 HFO-1132(E) Mass % 25.0 30.0 35.0 40.0 10.0 15.0 20.0 25.0HFO-1123 Mass % 18.1 13.1 8.1 3.1 28.1 23.1 18.1 13.1 R1234yf Mass %35.0 35.0 35.0 35.0 40.0 40.0 40.0 40.0 R32 Mass % 21.9 21.9 21.9 21.921.9 21.9 21.9 21.9 GWP — 150 150 150 150 150 150 150 150 COP ratio %(relative 98.4 98.7 99.0 99.3 98.3 98.5 98.7 99.0 to R410A)Refrigerating % (relative 92.9 92.4 91.9 91.3 90.8 90.5 90.2 89.7capacity ratio to R410A)

TABLE 82 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Comp. Item Unit 220 221 222 223 224225 226 Ex. 101 HFO-1132(E) Mass % 30.0 35.0 10.0 15.0 20.0 25.0 30.010.0 HFO-1123 Mass % 8.1 3.1 23.1 18.1 13.1 8.1 3.1 18.1 R1234yf Mass %40.0 40.0 45.0 45.0 45.0 45.0 45.0 50.0 R32 Mass % 21.9 21.9 21.9 21.921.9 21.9 21.9 21.9 GWP — 150 150 150 150 150 150 150 150 COP ratio %(relative 99.3 99.6 98.9 99.1 99.3 99.6 99.9 99.6 to R410A)Refrigerating % (relative 89.3 88.8 87.6 87.3 87.0 86.6 86.2 84.4capacity ratio to R410A)

TABLE 83 Comp. Comp. Comp. Item Unit Ex. 102 Ex. 103 Ex. 104 HFO-1132(E)Mass % 15.0 20.0 25.0 HFO-1123 Mass % 13.1 8.1 3.1 R1234yf Mass % 50.050.0 50.0 R32 Mass % 21.9 21.9 21.9 GWP — 150 150 150 COP ratio %(relative 99.8 100.0 100.2 to R410A) Refrigerating % (relative 84.1 83.883.4 capacity ratio to R410A)

TABLE 84 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Comp. Item Unit 227 228 229 230 231232 233 Ex. 105 HFO-1132(E) Mass % 10.0 15.0 20.0 25.0 30.0 35.0 40.045.0 HFO-1123 Mass % 55.7 50.7 45.7 40.7 35.7 30.7 25.7 20.7 R1234yfMass % 5.0 5.0 5.0 5.0 5.0 5.0 5.0 5.0 R32 Mass % 29.3 29.3 29.3 29.329.3 29.3 29.3 29.3 GWP — 199 199 199 199 199 199 199 199 COP ratio %(relative 95.9 96.0 96.2 96.3 96.6 96.8 97.1 97.3 to R410A)Refrigerating % (relative 112.2 111.9 111.6 111.2 110.7 110.2 109.6109.0 capacity ratio to R410A)

TABLE 85 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Comp. Item Unit 234 235 236 237 238239 240 Ex. 106 HFO-1132(E) Mass % 10.0 15.0 20.0 25.0 30.0 35.0 40.045.0 HFO-1123 Mass % 50.7 45.7 40.7 35.7 30.7 25.7 20.7 15.7 R1234yfMass % 10.0 10.0 10.0 10.0 10.0 10.0 10.0 10.0 R32 Mass % 29.3 29.3 29.329.3 29.3 29.3 29.3 29.3 GWP — 199 199 199 199 199 199 199 199 COP ratio% (relative 96.3 96.4 96.6 96.8 97.0 97.2 97.5 97.8 to R410A)Refrigerating % (relative 109.4 109.2 108.8 108.4 107.9 107.4 106.8106.2 capacity ratio to R410A)

TABLE 86 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Comp. Item Unit 241 242 243 244 245246 247 Ex. 107 HFO-1132(E) Mass % 10.0 15.0 20.0 25.0 30.0 35.0 40.045.0 HFO-1123 Mass % 45.7 40.7 35.7 30.7 25.7 20.7 15.7 10.7 R1234yfMass % 15.0 15.0 15.0 15.0 15.0 15.0 15.0 15.0 R32 Mass % 29.3 29.3 29.329.3 29.3 29.3 29.3 29.3 GWP — 199 199 199 199 199 199 199 199 COP ratio% (relative 96.7 96.8 97.0 97.2 97.4 97.7 97.9 98.2 to R410A)Refrigerating % (relative 106.6 106.3 106.0 105.5 105.1 104.5 104.0103.4 capacity ratio to R410A)

TABLE 87 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Comp. Item Unit 248 249 250 251 252253 254 Ex. 108 HFO-1132(E) Mass % 10.0 15.0 20.0 25.0 30.0 35.0 40.045.0 HFO-1123 Mass % 40.7 35.7 30.7 25.7 20.7 15.7 10.7 5.7 R1234yf Mass% 20.0 20.0 20.0 20.0 20.0 20.0 20.0 20.0 R32 Mass % 29.3 29.3 29.3 29.329.3 29.3 29.3 29.3 GWP — 199 199 199 199 199 199 199 199 COP ratio %(relative 97.1 97.3 97.5 97.7 97.9 98.1 98.4 98.7 to R410A)Refrigerating % (relative 103.7 103.4 103.0 102.6 102.2 101.6 101.1100.5 capacity ratio to R410A)

TABLE 88 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 255 256 257 258 259260 261 262 HFO-1132(E) Mass % 10.0 15.0 20.0 25.0 30.0 35.0 40.0 10.0HFO-1123 Mass % 35.7 30.7 25.7 20.7 15.7 10.7 5.7 30.7 R1234yf Mass %25.0 25.0 25.0 25.0 25.0 25.0 25.0 30.0 R32 Mass % 29.3 29.3 29.3 29.329.3 29.3 29.3 29.3 GWP — 199 199 199 199 199 199 199 199 COP ratio %(relative 97.6 97.7 97.9 98.1 98.4 98.6 98.9 98.1 to R410A)Refrigerating % (relative 100.7 100.4 100.1 99.7 99.2 98.7 98.2 97.7capacity ratio to R410A)

TABLE 89 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 263 264 265 266 267268 269 270 HFO-1132(E) Mass % 15.0 20.0 25.0 30.0 35.0 10.0 15.0 20.0HFO-1123 Mass % 25.7 20.7 15.7 10.7 5.7 25.7 20.7 15.7 R1234yf Mass %30.0 30.0 30.0 30.0 30.0 35.0 35.0 35.0 R32 Mass % 29.3 29.3 29.3 29.329.3 29.3 29.3 29.3 GWP — 199 199 199 199 199 200 200 200 COP ratio %(relative 98.2 98.4 98.6 98.9 99.1 98.6 98.7 98.9 to R410A)Refrigerating % (relative 97.4 97.1 96.7 96.2 95.7 94.7 94.4 94.0capacity ratio to R410A)

TABLE 90 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 271 272 273 274 275276 277 278 HFO-1132(E) Mass % 25.0 30.0 10.0 15.0 20.0 25.0 10.0 15.0HFO-1123 Mass % 10.7 5.7 20.7 15.7 10.7 5.7 15.7 10.7 R1234yf Mass %35.0 35.0 40.0 40.0 40.0 40.0 45.0 45.0 R32 Mass % 29.3 29.3 29.3 29.329.3 29.3 29.3 29.3 GWP — 200 200 200 200 200 200 200 200 COP ratio %(relative 99.2 99.4 99.1 99.3 99.5 99.7 99.7 99.8 to R410A)Refrigerating % (relative 93.6 93.2 91.5 91.3 90.9 90.6 88.4 88.1capacity ratio to R410A)

TABLE 91 Comp. Comp. Item Unit Ex. 279 Ex. 280 Ex. 109 Ex. 110HFO-1132(E) Mass % 20.0 10.0 15.0 10.0 HFO-1123 Mass % 5.7 10.7 5.7 5.7R1234yf Mass % 45.0 50.0 50.0 55.0 R32 Mass % 29.3 29.3 29.3 29.3 GWP —200 200 200 200 COP ratio % (relative 100.0 100.3 100.4 100.9 to R410A)Refrigerating % (relative 87.8 85.2 85.0 82.0 capacity ratio to R410A)

TABLE 92 Ex. Ex. Ex. Ex. Ex. Comp. Ex. Ex. Item Unit 281 282 283 284 285Ex. 111 286 287 HFO-1132(E) Mass % 10.0 15.0 20.0 25.0 30.0 35.0 10.015.0 HFO-1123 Mass % 40.9 35.9 30.9 25.9 20.9 15.9 35.9 30.9 R1234yfMass % 5.0 5.0 5.0 5.0 5.0 5.0 10.0 10.0 R32 Mass % 44.1 44.1 44.1 44.144.1 44.1 44.1 44.1 GWP — 298 298 298 298 298 298 299 299 COP ratio %(relative 97.8 97.9 97.9 98.1 98.2 98.4 98.2 98.2 to R410A)Refrigerating % (relative 112.5 112.3 111.9 111.6 111.2 110.7 109.8109.5 capacity ratio to R410A)

TABLE 93 Ex. Ex. Ex. Comp. Ex. Ex. Ex. Ex. Item Unit 288 289 290 Ex. 112291 292 293 294 HFO-1132(E) Mass % 20.0 25.0 30.0 35.0 10.0 15.0 20.025.0 HFO-1123 Mass % 25.9 20.9 15.9 10.9 30.9 25.9 20.9 15.9 R1234yfMass % 10.0 10.0 10.0 10.0 15.0 15.0 15.0 15.0 R32 Mass % 44.1 44.1 44.144.1 44.1 44.1 44.1 44.1 GWP — 299 299 299 299 299 299 299 299 COP ratio% (relative 98.3 98.5 98.6 98.8 98.6 98.6 98.7 98.9 to R410A)Refrigerating % (relative 109.2 108.8 108.4 108.0 107.0 106.7 106.4106.0 capacity ratio to R410A)

TABLE 94 Ex. Comp. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 295 Ex. 113 296 297298 299 300 301 HFO-1132(E) Mass % 30.0 35.0 10.0 15.0 20.0 25.0 30.010.0 HFO-1123 Mass % 10.9 5.9 25.9 20.9 15.9 10.9 5.9 20.9 R1234yf Mass% 15.0 15.0 20.0 20.0 20.0 20.0 20.0 25.0 R32 Mass % 44.1 44.1 44.1 44.144.1 44.1 44.1 44.1 GWP — 299 299 299 299 299 299 299 299 COP ratio %(relative 99.0 99.2 99.0 99.0 99.2 99.3 99.4 99.4 to R410A)Refrigerating % (relative 105.6 105.2 104.1 103.9 103.6 103.2 102.8101.2 capacity ratio to R410A)

TABLE 95 Ex. Ex. Ex. Ex. Ex. Ex. Ex. Ex. Item Unit 302 303 304 305 306307 308 309 HFO-1132(E) Mass % 15.0 20.0 25.0 10.0 15.0 20.0 10.0 15.0HFO-1123 Mass % 15.9 10.9 5.9 15.9 10.9 5.9 10.9 5.9 R1234yf Mass % 25.025.0 25.0 30.0 30.0 30.0 35.0 35.0 R32 Mass % 44.1 44.1 44.1 44.1 44.144.1 44.1 44.1 GWP — 299 299 299 299 299 299 299 299 COP ratio %(relative 99.5 99.6 99.7 99.8 99.9 100.0 100.3 100.4 to R410A)Refrigerating % (relative 101.0 100.7 100.3 98.3 98.0 97.8 95.3 95.1capacity ratio to R410A)

TABLE 96 Item Unit Ex. 400 HFO-1132(E) Mass % 10.0 HFO-1123 Mass % 5.9R1234yf Mass % 40.0 R32 Mass % 44.1 GWP — 299 COP ratio % (relative toR410A) 100.7 Refrigerating capacity ratio % (relative to R410A) 92.3

The above results indicate that the refrigerating capacity ratiorelative to R410A is 85% or more in the following cases:

When the mass % of HFO-1132(E), HFO-1123, R1234yf, and R32 based ontheir sum is respectively represented by x, y, z, and a, in a ternarycomposition diagram in which the sum of HFO-1132(E), HFO-1123, andR1234yf is (100−a) mass %, a straight line connecting a point (0.0,100.0−a, 0.0) and a point (0.0, 0.0, 100.0−a) is the base, and the point(0.0, 100.0−a, 0.0) is on the left side, if 0<a≤11.1, coordinates(x,y,z) in the ternary composition diagram are on, or on the left sideof, a straight line AB that connects point A (0.0134a²−1.9681a+68.6,0.0, −0.0134a²+0.9681a+31.4) and point B (0.0, 0.0144a²−1.6377a+58.7,−0.0144a²+0.6377a+41.3);

if 11.1<a≤18.2, coordinates (x,y,z) in the ternary composition diagramare on, or on the left side of, a straight line AB that connects point A(0.0112a²−1.9337a+68.484, 0.0, −0.0112a²+0.9337a+31.516) and point B(0.0, 0.0075a²−1.5156a+58.199, −0.0075a²+0.5156a+41.801);

if 18.2a<a≤26.7, coordinates (x,y,z) in the ternary composition diagramare on, or on the left side of, a straight line AB that connects point A(0.0107a²−1.9142a+68.305, 0.0, −0.0107a²+0.9142a+31.695) and point B(0.0, 0.009a²−1.6045a+59.318, −0.009a²+0.6045a+40.682);

if 26.7<a≤36.7, coordinates (x,y,z) in the ternary composition diagramare on, or on the left side of, a straight line AB that connects point A(0.0103a²−1.9225a+68.793, 0.0, −0.0103a²+0.9225a+31.207) and point B(0.0, 0.0046a²−1.41a+57.286, −0.0046a²+0.41a+42.714); and

if 36.7<a≤46.7, coordinates (x,y,z) in the ternary composition diagramare on, or on the left side of, a straight line AB that connects point A(0.0085a²−1.8102a+67.1, 0.0, −0.0085a²+0.8102a+32.9) and point B (0.0,0.0012a²−1.1659a+52.95, −0.0012a²+0.1659a+47.05).

Actual points having a refrigerating capacity ratio of 85% or more forma curved line that connects point A and point B in FIG. 3, and thatextends toward the 1234yf side. Accordingly, when coordinates are on, oron the left side of, the straight line AB, the refrigerating capacityratio relative to R410A is 85% or more.

Similarly, it was also found that in the ternary composition diagram, if0<a≤11.1, when coordinates (x,y,z) are on, or on the left side of, astraight line D′C that connects point D′ (0.0, 0.0224a²+0.968a+75.4,−0.0224a²−1.968a+24.6) and point C (−0.2304a²−0.4062a+32.9,0.2304a²−0.5938a+67.1, 0.0); or if 11.1<a≤46.7, when coordinates are inthe entire region, the COP ratio relative to that of R410A is 92.5% ormore.

In FIG. 3, the COP ratio of 92.5% or more forms a curved line CD. InFIG. 3, an approximate line formed by connecting three points: point C(32.9, 67.1, 0.0) and points (26.6, 68.4, 5) (19.5, 70.5, 10) where theCOP ratio is 92.5% when the concentration of R1234yf is 5 mass % and 10mass was obtained, and a straight line that connects point C and pointD′ (0, 75.4, 24.6), which is the intersection of the approximate lineand a point where the concentration of HFO-1132(E) is 0.0 mass % wasdefined as a line segment D′C. In FIG. 4, point D′(0, 83.4, 9.5) wassimilarly obtained from an approximate curve formed by connecting pointC (18.4, 74.5, 0) and points (13.9, 76.5, 2.5) (8.7, 79.2, 5) where theCOP ratio is 92.5%, and a straight line that connects point C and pointD′ was defined as the straight line D′C.

The composition of each mixture was defined as WCF. A leak simulationwas performed using NIST Standard Reference Database REFLEAK Version 4.0under the conditions of Equipment, Storage, Shipping, Leak, and Rechargeaccording to the ASHRAE Standard 34-2013. The most flammable fractionwas defined as WCFF.

For the flammability, the burning velocity was measured according to theANSI/ASHRAE Standard 34-2013. Both WCF and WCFF having a burningvelocity of 10 cm/s or less were determined to be classified as “Class2L (lower flammability).”

A burning velocity test was performed using the apparatus shown in FIG.1 in the following manner. First, the mixed refrigerants used had apurity of 99.5% or more, and were degassed by repeating a cycle offreezing, pumping, and thawing until no traces of air were observed onthe vacuum gauge. The burning velocity was measured by the closedmethod. The initial temperature was ambient temperature. Ignition wasperformed by generating an electric spark between the electrodes in thecenter of a sample cell. The duration of the discharge was 1.0 to 9.9ms, and the ignition energy was typically about 0.1 to 1.0 J. The spreadof the flame was visualized using schlieren photographs. A cylindricalcontainer (inner diameter: 155 mm, length: 198 mm) equipped with twolight transmission acrylic windows was used as the sample cell, and axenon lamp was used as the light source. Schlieren images of the flamewere recorded by a high-speed digital video camera at a frame rate of600 fps and stored on a PC.

The results are shown in Tables 97 to 104.

TABLE 97 Comp. Comp. Comp. Comp. Comp. Comp. Item Ex. 6 Ex. 13 Ex. 19Ex. 24 Ex. 29 Ex. 34 WCF HFO-1132(E) Mass % 72.0 60.9 55.8 52.1 48.645.4 HFO-1123 Mass % 28.0 32.0 33.1 33.4 33.2 32.7 R1234yf Mass % 0.00.0 0.0 0 0 0 R32 Mass % 0.0 7.1 11.1 14.5 18.2 21.9 Burning velocity(WCF) cm/s 10 10 10 10 10 10

TABLE 98 Comp. Comp. Comp. Comp. Comp. Item Ex. 39 Ex. 45 Ex. 51 Ex. 57Ex. 62 WCF HFO-1132(E) Mass % 41.8 40 35.7 32 30.4 HFO-1123 Mass % 31.530.7 23.6 23.9 21.8 R1234yf Mass % 0 0 0 0 0 R32 Mass % 26.7 29.3 36.744.1 47.8 Burning velocity (WCF) cm/s 10 10 10 10 10

TABLE 99 Comp. Comp. Comp. Comp. Comp. Comp. Item Ex. 7 Ex. 14 Ex. 20Ex. 25 Ex. 30 Ex. 35 WCF HFO-1132(E) Mass % 72.0 60.9 55.8 52.1 48.645.4 HFO-1123 Mass % 0.0 0.0 0.0 0 0 0 R1234yf Mass % 28.0 32.0 33.133.4 33.2 32.7 R32 Mass % 0.0 7.1 11.1 14.5 18.2 21.9 Burning velocity(WCF) cm/s 10 10 10 10 10 10

TABLE 100 Comp. Comp. Comp. Comp. Comp. Item Ex. 40 Ex. 46 Ex. 52 Ex. 58Ex. 63 WCF HFO-1132(E) Mass % 41.8 40 35.7 32 30.4 HFO-1123 Mass % 0 0 00 0 R1234yf Mass % 31.5 30.7 23.6 23.9 21.8 R32 Mass % 26.7 29.3 36.744.1 47.8 Burning velocity (WCF) cm/s 10 10 10 10 10

TABLE 101 Item Comp. Ex. 8 Comp. Ex. 15 Comp. Ex. 21 Comp. Ex. 26 Comp.Ex. 31 Comp. Ex. 36 WCF HFO-1132 (E) Mass % 47.1 40.5 37.0 34.3 32.030.3 HFO-1123 Mass % 52.9 52.4 51.9 51.2 49.8 47.8 R1234yf Mass % 0.00.0 0.0 0.0 0.0 0.0 R32 Mass % 0.0 7.1 11.1 14.5 18.2 21.9 Leakcondition that results Storage/ Storage/ Storage/ Storage/ Storage/Storage/ in WCFF Shipping −40° C., Shipping −40° C., Shipping −40° C.,Shipping −40° C., Shipping −40° C., Shipping −40° C., 92% release, 92%release, 92% release, 92% release, 92% release, 92% release, liquidphase liquid phase liquid phase liquid phase liquid phase liquid phaseside side side side side side WCFF HFO-1132 (E) Mass % 72.0 62.4 56.250.6 45.1 40.0 HFO-1123 Mass % 28.0 31.6 33.0 33.4 32.5 30.5 R1234yfMass % 0.0 0.0 0.0 20.4 0.0 0.0 R32 Mass % 0.0 50.9 10.8 16.0 22.4 29.5Burning velocity cm/s 8 or less 8 or less 8 or less 8 or less 8 or less8 or less (WCF) Burning velocity cm/s 10 10 10 10 10 10 (WCFF)

TABLE 102 Comp. Comp. Comp. Comp. Comp. Item Ex. 41 Ex. 47 Ex. 53 Ex. 59Ex. 64 WCF HFO-1132(E) Mass % 29.1 28.8 29.3 29.4 28.9 HFO-1123 Mass %44.2 41.9 34.0 26.5 23.3 R1234yf Mass % 0.0 0.0 0.0 0.0 0.0 R32 Mass %26.7 29.3 36.7 44.1 47.8 Leak condition that results Storage/ Storage/Storage/ Storage/ Storage/ in WCFF Shipping −40° Shipping −40° Shipping−40° Shipping −40° Shipping −40° C., 92% release, C., 92% release, C.,92% release, C., 90% release, C., 86% release, liquid phase liquid phaseliquid phase gas phase gas phase side side side side side WCFFHFO-1132(E) Mass % 34.6 32.2 27.7 28.3 27.5 HFO-1123 Mass % 26.5 23.917.5 18.2 16.7 R1234yf Mass % 0.0 0.0 0.0 0.0 0.0 R32 Mass % 38.9 43.954.8 53.5 55.8 Burning velocity cm/s 8 or less 8 or less 8.3 9.3 9.6(WCF) Burning velocity cm/s 10 10 10 10 10 (WCFF)

TABLE 103 Comp. Comp. Comp. Comp. Comp. Comp. Item Ex. 9 Ex. 16 Ex. 22Ex. 27 Ex. 32 Ex. 37 WCF HFO-1132(E) Mass % 61.7 47.0 41.0 36.5 32.528.8 HFO-1123 Mass % 5.9 7.2 6.5 5.6 4.0 2.4 R1234yf Mass % 32.4 38.741.4 43.4 45.3 46.9 R32 Mass % 0.0 7.1 11.1 14.5 18.2 21.9 Leakcondition that results Storage/ Storage/ Storage/ Storage/ Storage/Storage/ in WCFF Shipping −40° Shipping −40° Shipping −40° Shipping −40°Shipping −40° Shipping −40° C., 0% release, C., 0% release, C., 0%release, C., 92% release, C., 0% release, C., 0% release, gas phase gasphase gas phase liquid gas phase gas phase side side side phase sideside side WCFF HFO-1132(E) Mass % 72.0 56.2 50.4 46.0 42.4 39.1 HFO-1123Mass % 10.5 12.6 11.4 10.1 7.4 4.4 R1234yf Mass % 17.5 20.4 21.8 22.924.3 25.7 R32 Mass % 0.0 10.8 16.3 21.0 25.9 30.8 Burning velocity cm/s8 or less 8 or less 8 or less 8 or less 8 or less 8 or less (WCF)Burning velocity cm/s 10 10 10 10 10 10 (WCFF)

TABLE 104 Comp. Comp. Comp. Comp. Comp. Item Ex. 42 Ex. 48 Ex. 54 Ex. 60Ex. 65 WCF HFO-1132(E) Mass % 24.8 24.3 22.5 21.1 20.4 HFO-1123 Mass %0.0 0.0 0.0 0.0 0.0 R1234yf Mass % 48.5 46.4 40.8 34.8 31.8 R32 Mass %26.7 29.3 36.7 44.1 47.8 Leak conditions that results Storage/ Storage/Storage/ Storage/ Storage/ in WCFF Shipping −40° Shipping −40° Shipping−40° Shipping −40° Shipping −40° C., 0% release, C., 0% release, C., 0%release, C., 0% release, C., 0% release, gas phase gas phase gas phasegas phase gas phase side side side side side WCFF HFO-1132(E) Mass %35.3 34.3 31.3 29.1 28.1 HFO-1123 Mass % 0.0 0.0 0.0 0.0 0.0 R1234yfMass % 27.4 26.2 23.1 19.8 18.2 R32 Mass % 37.3 39.6 45.6 51.1 53.7Burning velocity cm/s 8 or less 8 or less 8 or less 8 or less 8 or less(WCF) Burning velocity cm/s 10 10 10 10 10 (WCFF)

The results in Tables 97 to 100 indicate that the refrigerant has a WCFlower flammability in the following cases:

When the mass % of HFO-1132(E), HFO-1123, R1234yf, and R32 based ontheir sum in the mixed refrigerant of HFO-1132(E), HFO-1123, R1234yf,and R32 is respectively represented by x, y, z, and a, coordinates(x,y,z) in a ternary composition diagram in which the sum ofHFO-1132(E), HFO-1123, and R1234yf is (100−a) mass % and a straight lineconnecting a point (0.0, 100.0−a, 0.0) and a point (0.0, 0.0, 100.0−a)is the base, if 0<a≤11.1, coordinates (x,y,z) in the ternary compositiondiagram are on or below a straight line GI that connects point G(0.026a²−1.7478a+72.0, −0.026a²+0.7478a+28.0, 0.0) and point I(0.026a²−1.7478a+72.0, 0.0, −0.026a²+0.7478a+28.0);

if 11.1<a≤18.2, coordinates (x,y,z) in the ternary composition diagramare on or below a straight line GI that connects point G(0.02a²−1.6013a+71.105, −0.02a²+0.6013a+28.895, 0.0) and point I(0.02a²−1.6013a+71.105, 0.0, −0.02a²+0.6013a+28.895); if 18.2<a≤26.7,coordinates (x,y,z) in the ternary composition diagram are on or below astraight line GI that connects point G (0.0135a²−1.4068a+69.727,−0.0135a²+0.4068a+30.273, 0.0) and point I (0.0135a²−1.4068a+69.727,0.0, −0.0135a²+0.4068a+30.273); if 26.7<a≤36.7, coordinates (x,y,z) inthe ternary composition diagram are on or below a straight line GI thatconnects point G (0.0111a²−1.3152a+68.986, −0.0111a²+0.3152a+31.014,0.0) and point I (0.0111a²−1.3152a+68.986, 0.0,−0.0111a²+0.3152a+31.014); and if 36.7<a≤46.7, coordinates (x,y,z) inthe ternary composition diagram are on or below a straight line GI thatconnects point G (0.0061a²−0.9918a+63.902, −0.0061a²−0.0082a+36.098,0.0)and point I (0.0061a² 0.9918a+63.902, 0.0, −0.0061a²−0.0082a+36.098).

Three points corresponding to point G (Table 105) and point I (Table106) were individually obtained in each of the following five ranges bycalculation, and their approximate expressions were obtained.

TABLE 105 Item 11.1 ≥ R32 > 0 18.2 ≥ R32 ≥ 11.1 26.7 ≥ R32 ≥ 18.2 R32 07.1 11.1 11.1 14.5 18.2 18.2 21.9 26.7 HFO-1132(E) 72.0 60.9 55.8 55.852.1 48.6 48.6 45.4 41.8 HFO-1123 28.0 32.0 33.1 33.1 33.4 33.2 33.232.7 31.5 R1234yf 0 0 0 0 0 0 0 0 0 R32 a a a HFO-1132(E)  0.026a² −1.7478a + 72.0  0.02a² − 1.6013a + 71.105  0.0135a² − 1.4068a + 69.727Approximate expression HFO-1123 −0.026a² + 0.7478a + 28.0 −0.02a² +0.6013a + 28.895 −0.0135a² + 0.4068a + 30.273 Approximate expressionR1234yf 0 0 0 Approximate expression Item 36.7 ≥ R32 ≥ 26.7 46.7 ≥ R32 ≥36.7 R32 26.7 29.3 36.7 36.7 44.1 47.8 HFO-1132(E) 41.8 40.0 35.7 35.732.0 30.4 HFO-1123 31.5 30.7 27.6 27.6 23.9 21.8 R1234yf 0 0 0 0 0 0 R32a a HFO-1132(E)  0.0111a2 − 1.3152a + 68.986  0.0061a² − 0.9918a +63.902 Approximate expression HFO-1123 −0.0111a2 + 0.3152a + 31.014−0.0061a² − 0.0082a + 36.098 Approximate expression R1234yf 0 0Approximate expression

TABLE 106 Item 11.1 ≥ R32 > 0 18.2 ≥ R32 ≥ 11.1 26.7 ≥ R32 ≥ 18.2 R32 07.1 11.1 11.1 14.5 18.2 18.2 21.9 26.7 HFO-1132(E) 72.0 60.9 55.8 55.852.1 48.6 48.6 45.4 41.8 HFO-1123 0 0 0 0 0 0 0 0 0 R1234yf 28.0 32.033.1 33.1 33.4 33.2 33.2 32.7 31.5 R32 a a a HFO-1132(E)  0.026a² −1.7478a + 72.0  0.02a² − 1.6013a + 71.105  0.0135a² − 1.4068a + 69.727Approximate expression HFO-1123 0 0 0 Approximate expression R1234yf−0.026a² + 0.7478a + 28.0 −0.02a² + 0.6013a + 28.895 −0.0135a² +0.4068a + 30.273 Approximate expression Item 36.7 ≥ R32 ≥ 26.7 46.7 ≥R32 ≥ 36.7 R32 26.7 29.3 36.7 36.7 44.1 47.8 HFO-1132(E) 41.8 40.0 35.735.7 32.0 30.4 HFO-1123 0 0 0 0 0 0 R1234yf 31.5 30.7 23.6 23.6 23.521.8 R32 x x HFO-1132(E)  0.0111a² − 1.3152a + 68.986  0.0061a² −0.9918a + 63.902 Approximate expression HFO-1123 0 0 Approximateexpression R1234yf −0.0111a² + 0.3152a + 31.014 −0.0061a² − 0.0082a +36.098 Approximate expression

The results in Tables 101 to 104 indicate that the refrigerant isdetermined to have a WCFF lower flammability, and the flammabilityclassification according to the ASHRAE Standard is “2L (flammability)”in the following cases:

When the mass % of HFO-1132(E), HFO-1123, R1234yf, and R32 based ontheir sum in the mixed refrigerant of HFO-1132(E), HFO-1123, R1234yf,and R32 is respectively represented by x, y, z, and a, in a ternarycomposition diagram in which the sum of HFO-1132(E), HFO-1123, andR1234yf is (100−a) mass % and a straight line connecting a point (0.0,100.0−a, 0.0) and a point (0.0, 0.0, 100.0−a) is the base, if 0<a≤11.1,coordinates (x,y,z) in the ternary composition diagram are on or below astraight line JK′ that connects point J (0.0049a²−0.9645a+47.1,−0.0049a²−0.0355a+52.9, 0.0) and point K′(0.0514a²−2.4353a+61.7,−0.0323a²+0.4122a+5.9, −0.0191a²+1.0231a+32.4); if 11.1<a≤18.2,coordinates are on a straight line JK′ that connects point J(0.0243a²−1.4161a+49.725, −0.0243a²+0.4161a+50.275, 0.0) and pointK′(0.0341a²−2.1977a+61.187, −0.0236a²+0.34a+5.636,−0.0105a²+0.8577a+33.177); if 18.2<a≤26.7, coordinates are on or below astraight line JK′ that connects point J (0.0246a²−1.4476a+50.184,−0.0246a²+0.4476a+49.816, 0.0) and point K′ (0.0196a²−1.7863a+58.515,−0.0079a²−0.1136a+8.702, −0.0117a²+0.8999a+32.783); if 26.7<a≤36.7,coordinates are on or below a straight line JK′ that connects point J(0.0183a²−1.1399a+46.493, −0.0183a²+0.1399a+53.507, 0.0) and point K′(−0.0051a²+0.0929a+25.95, 0.0, 0.0051a²−1.0929a+74.05); and if36.7<a≤46.7, coordinates are on or below a straight line JK′ thatconnects point J (−0.0134a²+1.0956a+7.13, 0.0134a²−2.0956a+92.87, 0.0)and point K′(−1.892a+29.443, 0.0, 0.892a+70.557).

Actual points having a WCFF lower flammability form a curved line thatconnects point J and point K′ (on the straight line AB) in FIG. 3 andextends toward the HFO-1132(E) side. Accordingly, when coordinates areon or below the straight line JK′, WCFF lower flammability is achieved.

Three points corresponding to point J (Table 107) and point K′ (Table108) were individually obtained in each of the following five ranges bycalculation, and their approximate expressions were obtained.

TABLE 107 Item 11.1 ≥ R32 > 0 18.2 ≥ R32 ≥ 11.1 26.7 ≥ R32 ≥ 18.2 R32 07.1 11.1 11.1 14.5 18.2 18.2 21.9 26.7 HFO-1132(E) 47.1 40.5 37 37.034.3 32.0 32.0 30.3 29.1 HFO-1123 52.9 52.4 51.9 51.9 51.2 49.8 49.847.8 44.2 R1234yf 0 0 0 0 0 0 0 0 0 R32 a a a HFO-1132(E)  0.0049a² −0.9645a + 47.1  0.0243a² − 1.4161a + 49.725  0.0246a² − 1.4476a + 50.184Approximate expression HFO-1123 −0.0049a² − 0.0355a + 52.9 −0.0243a² +0.4161a + 50.275 −0.0246a² + 0.4476a + 49.816 Approximate expressionR1234yf 0 0 0 Approximate expression Item 36.7 ≥ R32 ≥ 26.7 47.8 ≥ R32 ≥36.7 R32 26.7 29.3 36.7 36.7 44.1 47.8 HFO-1132(E) 29.1 28.8 29.3 29.329.4 28.9 HFO-1123 44.2 41.9 34.0 34.0 26.5 23.3 R1234yf 0 0 0 0 0 0 R32a a HFO-1132(E)  0.0183a² − 1.1399a + 46.493 −0.0134a² + 1.0956a + 7.13 Approximate expression HFO-1123 −0.0183a² + 0.1399a + 53.507  0.0134a² −2.0956a + 92.87 Approximate expression R1234yf 0 0 Approximateexpression

TABLE 108 Item 11.1 ≥ R32 > 0 18.2 ≥ R32 ≥ 11.1 26.7 ≥ R32 ≥ 18.2 R32 07.1 11.1 11.1 14.5 18.2 18.2 21.9 26.7 HFO-1132(E) 61.7 47.0 41.0 41.036.5 32.5 32.5 28.8 24.8 HFO-1123 5.9 7.2 6.5 6.5 5.6 4.0 4.0 2.4 0R1234yf 32.4 38.7 41.4 41.4 43.4 45.3 45.3 46.9 48.5 R32 x x xHFO-1132(E)  0.0514a² − 2.4353a + 61.7  0.0341a² − 2.1977a + 61.187 0.0196a² − 1.7863a + 58.515 Approximate expression HFO-1123 −0.0323a² +0.4122a + 5.9  −0.0236a² + 0.34a + 5.636  −0.0079a² − 0.1136a + 8.702 Approximate expression R1234yf −0.0191a² + 1.0231a + 32.4 −0.0105a² +0.8577a + 33.177 −0.0117a² + 0.8999a + 32.783 Approximate expressionItem 36.7 ≥ R32 ≥ 26.7 46.7 ≥ R32 ≥ 36.7 R32 26.7 29.3 36.7 36.7 44.147.8 HFO-1132(E) 24.8 24.3 22.5 22.5 21.1 20.4 HFO-1123 0 0 0 0 0 0R1234yf 48.5 46.4 40.8 40.8 34.8 31.8 R32 x x HFO-1132(E) −0.0051a² +0.0929a + 25.95 −1.892a + 29.443 Approximate expression HFO-1123 0 0Approximate expression R1234yf  0.0051a² − 1.0929a + 74.05  0.892a +70.557 Approximate expression

FIGS. 3 to 13 show compositions whose R32 content a (mass %) is 0 mass%, 7.1 mass %, 11.1 mass %, 14.5 mass %, 18.2 mass %, 21.9 mass %, 26.7mass %, 29.3 mass %, 36.7 mass %, 44.1 mass %, and 47.8 mass %,respectively.

Points A, B, C, and D′ were obtained in the following manner accordingto approximate calculation.

Point A is a point where the content of HFO-1123 is 0 mass %, and arefrigerating capacity ratio of 85% relative to that of R410A isachieved. Three points corresponding to point A were obtained in each ofthe following five ranges by calculation, and their approximateexpressions were obtained (Table 109).

TABLE 109 Item 11.1 ≥ R32 > 0 18.2 ≥ R32 ≥ 11.1 26.7 ≥ R32 ≥ 18.2 R32 07.1 11.1 11.1 14.5 18.2 18.2 21.9 26.7 HFO-1132(E) 68.6 55.3 48.4 48.442.8 37 37 31.5 24.8 HFO-1123 0 0 0 0 0 0 0 0 0 R1234yf 31.4 37.6 40.540.5 42.7 44.8 44.8 46.6 48.5 R32 a a a HFO-1132(E)  0.0134a² −1.9681a + 68.6  0.0112a² − 1.9337a + 68.484  0.0107a² − 1.9142a + 68.305Approximate expression HFO-1123 0 0 0 Approximate expression R1234yf−0.0134a² + 0.9681a + 31.4 −0.0112a² + 0.9337a + 31.516 −0.0107a² +0.9142a + 31.695 Approximate expression Item 36.7 ≥ R32 ≥ 26.7 46.7 ≥R32 ≥ 36.7 R32 26.7 29.3 36.7 36.7 44.1 47.8 HFO-1132(E) 24.8 21.3 12.112.1 3.8 0 HFO-1123 0 0 0 0 0 0 R1234yf 48.5 49.4 51.2 51.2 52.1 52.2R32 a a HFO-1132(E)  0.0103a² − 1.9225a + 68.793  0.0085a² − 1.8102a +67.1 Approximate expression HFO-1123 0 0 Approximate expression R1234yf−0.0103a² + 0.9225a + 31.207 −0.0085a² + 0.8102a + 32.9 Approximateexpression

Point B is a point where the content of HFO-1132(E) is 0 mass %, and arefrigerating capacity ratio of 85% relative to that of R410A isachieved.

Three points corresponding to point B were obtained in each of thefollowing five ranges by calculation, and their approximate expressionswere obtained (Table 110).

TABLE 110 Item 11.1 ≥ R32 > 0 18.2 ≥ R32 ≥ 11.1 26.7 ≥ R32 ≥ 18.2 R32 07.1 11.1 11.1 14.5 18.2 18.2 21.9 26.7 HFO-1132(E) 0 0 0 0 0 0 0 0 0HFO-1123 58.7 47.8 42.3 42.3 37.8 33.1 33.1 28.5 22.9 R1234yf 41.3 45.146.6 46.6 47.7 48.7 48.7 49.6 50.4 R32 a a a HFO-1132(E) 0 0 0Approximate expression HFO-1123  0.0144a² − 1.6377a + 58.7  0.0075a² −1.5156a + 58.199  0.009a² − 1.6045a + 59.318 Approximate expressionR1234yf −0.0144a² + 0.6377a + 41.3 −0.0075a² + 0.5156a + 41.801−0.009a² + 0.6045a + 40.682 Approximate expression Item 36.7 ≥ R32 ≥26.7 46.7 ≥ R32 ≥ 36.7 R32 26.7 29.3 36.7 36.7 44.1 47.8 HFO-1132(E) 0 00 0 0 0 HFO-1123 22.9 19.9 11.7 11.8 3.9 0 R1234yf 50.4 50.8 51.6 51.552.0 52.2 R32 a a HFO-1132(E) 0 0 Approximate expression HFO-1123 0.0046a² − 1.41a + 57.286  0.0012a² − 1.1659a + 52.95 Approximateexpression R1234yf −0.0046a² + 0.41a + 42.714 −0.0012a² + 0.1659a +47.05 Approximate expression

Point D′ is a point where the content of HFO-1132(E) is 0 mass %, and aCOP ratio of 95.5% relative to that of R410A is achieved.

Three points corresponding to point D′ were obtained in each of thefollowing by calculation, and their approximate expressions wereobtained (Table 111).

TABLE 111 Item 11.1 ≥ R32 > 0 R32 0 7.1 11.1 HFO-1132(E) 0 0 0 HFO-112375.4 83.4 88.9 R1234yf 24.6 9.5 0 R32 a HFO-1132(E) 0 Approximateexpression HFO-1123  0.0224a² + 0.968a + 75.4 Approximate expressionR1234yf −0.0224a² − 1.968a + 24.6 Approximate expression

Point C is a point where the content of R1234yf is 0 mass %, and a COPratio of 95.5% relative to that of R410A is achieved.

Three points corresponding to point C were obtained in each of thefollowing by calculation, and their approximate expressions wereobtained (Table 112).

TABLE 112 Item 11.1 ≥ R32 > 0 R32 0 7.1 11.1 HFO-1132(E) 32.9 18.4 0HFO-1123 67.1 74.5 88.9 R1234yf 0 0 0 R32 a HFO-1132(E) −0.2304a² −0.4062a + 32.9 Approximate expression HFO-1123  0.2304a² − 0.5938a +67.1 Approximate expression R1234yf 0 Approximate expression(5-4) Refrigerant D

The refrigerant D according to the present disclosure is a mixedrefrigerant comprising trans-1,2-difluoroethylene (HFO-1132(E)),difluoromethane (R32), and 2,3,3,3-tetrafluoro-1-propene (R1234yf).

The refrigerant D according to the present disclosure has variousproperties that are desirable as an R410A-alternative refrigerant; i.e.,a refrigerating capacity equivalent to that of R410A, a sufficiently lowGWP, and a lower flammability (Class 2L) according to the ASHRAEstandard.

The refrigerant D according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), R32, and R1234yf based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), R32, andR1234yf is 100 mass % are within the range of a figure surrounded byline segments J, JN, NE, and EI that connect the following 4 points:

point I (72.0, 0.0, 28.0),

point J (48.5, 18.3, 33.2),

point N (27.7, 18.2, 54.1), and

point E (58.3, 0.0, 41.7),

or on these line segments (excluding the points on the line segment EI);

the line segment IJ is represented by coordinates(0.0236y²−1.7616y+72.0, y, −0.0236y²+0.7616y+28.0);

the line segment NE is represented by coordinates (0.012y²−1.9003y+58.3,y, −0.012y²+0.9003y+41.7); and

the line segments JN and EI are straight lines. When the requirementsabove are satisfied, the refrigerant according to the present disclosurehas a refrigerating capacity ratio of 80% or more relative to R410A, aGWP of 125 or less, and a WCF lower flammability.

The refrigerant D according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), R32, and R1234yf based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), R32, andR1234yf is 100 mass % are within the range of a figure surrounded byline segments MM′, M′N, NV, VG, and GM that connect the following 5points:

point M (52.6, 0.0, 47.4),

point M′ (39.2, 5.0, 55.8),

point N (27.7, 18.2, 54.1),

point V (11.0, 18.1, 70.9), and

point G (39.6, 0.0, 60.4),

or on these line segments (excluding the points on the line segment GM);

the line segment MM′ is represented by coordinates (0.132y²−3.34y+52.6,y, −0.132y²+2.34y+47.4);

the line segment M′N is represented by coordinates (0.0596y²2.2541y+48.98, y, −0.0596y²+1.2541y+51.02);

the line segment VG is represented by coordinates(0.0123y²−1.8033y+39.6, y, −0.0123y²+0.8033y+60.4); and

the line segments NV and GM are straight lines. When the requirementsabove are satisfied, the refrigerant according to the present disclosurehas a refrigerating capacity ratio of 70% or more relative to R410A, aGWP of 125 or less, and an ASHRAE lower flammability.

The refrigerant D according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), R32, and R1234yf based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), R32, andR1234yf is 100 mass % are within the range of a figure surrounded byline segments ON, NU, and UO that connect the following 3 points:

point O (22.6, 36.8, 40.6),

point N (27.7, 18.2, 54.1), and

point U (3.9, 36.7, 59.4),

or on these line segments;

the line segment ON is represented by coordinates(0.0072y²−0.6701y+37.512, y, −0.0072y²−0.3299y+62.488);

the line segment NU is represented by coordinates(0.0083y²−1.7403y+56.635, y, −0.0083y²+0.7403y+43.365); and

the line segment UO is a straight line. When the requirements above aresatisfied, the refrigerant according to the present disclosure has arefrigerating capacity ratio of 80% or more relative to R410A, a GWP of250 or less, and an ASHRAE lower flammability.

The refrigerant D according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), R32, and R1234yf based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), R32, andR1234yf is 100 mass % are within the range of a figure surrounded byline segments QR, RT, TL, LK, and KQ that connect the following 5points:

point Q (44.6, 23.0, 32.4),

point R (25.5, 36.8, 37.7),

point T (8.6, 51.6, 39.8),

point L (28.9, 51.7, 19.4), and

point K (35.6, 36.8, 27.6),

or on these line segments;

the line segment QR is represented by coordinates(0.0099y²−1.975y+84.765, y, −0.0099y²+0.975y+15.235);

the line segment RT is represented by coordinates(0.0082y²−1.8683y+83.126, y, −0.0082y²+0.8683y+16.874);

the line segment LK is represented by coordinates(0.0049y²−0.8842y+61.488, y, −0.0049y²−0.1158y+38.512);

the line segment KQ is represented by coordinates(0.0095y²−1.2222y+67.676, y, −0.0095y²+0.2222y+32.324); and

the line segment TL is a straight line. When the requirements above aresatisfied, the refrigerant according to the present disclosure has arefrigerating capacity ratio of 92.5% or more relative to R410A, a GWPof 350 or less, and a WCF lower flammability.

The refrigerant D according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), R32, and R1234yf based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), R32, andR1234yf is 100 mass % are within the range of a figure surrounded byline segments PS, ST, and TP that connect the following 3 points:

point P (20.5, 51.7, 27.8),

point S (21.9, 39.7, 38.4), and

point T (8.6, 51.6, 39.8),

or on these line segments;

the line segment PS is represented by coordinates(0.0064y²−0.7103y+40.1, y, −0.0064y²−0.2897y+59.9);

the line segment ST is represented by coordinates(0.0082y²−1.8683y+83.126, y, −0.0082y²+0.8683y+16.874); and

the line segment TP is a straight line. When the requirements above aresatisfied, the refrigerant according to the present disclosure has arefrigerating capacity ratio of 92.5% or more relative to R410A, a GWPof 350 or less, and an ASHRAE lower flammability.

The refrigerant D according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), R32, and R1234yf based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), R32, andR1234yf is 100 mass % are within the range of a figure surrounded byline segments ac, cf, fd, and da that connect the following 4 points:

point a (71.1, 0.0, 28.9),

point c (36.5, 18.2, 45.3),

point f (47.6, 18.3, 34.1), and

point d (72.0, 0.0, 28.0),

or on these line segments;

the line segment ac is represented by coordinates(0.0181y²−2.2288y+71.096, y, −0.0181y²+1.2288y+28.904);

the line segment fd is represented by coordinates (0.02y²−1.7y+72, y,−0.02y²+0.7y+28); and

the line segments cf and da are straight lines. When the requirementsabove are satisfied, the refrigerant according to the present disclosurehas a refrigerating capacity ratio of 85% or more relative to R410A, aGWP of 125 or less, and a lower flammability (Class 2L) according to theASHRAE standard.

The refrigerant D according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), R32, and R1234yf based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), R32, andR1234yf is 100 mass % are within the range of a figure surrounded byline segments ab, be, ed, and da that connect the following 4 points:

point a (71.1, 0.0, 28.9),

point b (42.6, 14.5, 42.9),

point e (51.4, 14.6, 34.0), and

point d (72.0, 0.0, 28.0),

or on these line segments;

the line segment ab is represented by coordinates(0.0181y²−2.2288y+71.096, y, −0.0181y²+1.2288y+28.904);

the line segment ed is represented by coordinates (0.02y²−1.7y+72, y,−0.02y²+0.7y+28); and

the line segments be and da are straight lines. When the requirementsabove are satisfied, the refrigerant according to the present disclosurehas a refrigerating capacity ratio of 85% or more relative to R410A, aGWP of 100 or less, and a lower flammability (Class 2L) according to theASHRAE standard.

The refrigerant D according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), R32, and R1234yf based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), R32, andR1234yf is 100 mass % are within the range of a figure surrounded byline segments gi, ij, and jg that connect the following 3 points:

point g (77.5, 6.9, 15.6),

point i (55.1, 18.3, 26.6), and

point j (77.5. 18.4, 4.1),

or on these line segments;

the line segment gi is represented by coordinates(0.02y²−2.4583y+93.396, y, −0.02y²+1.4583y+6.604); and

the line segments ij and jg are straight lines. When the requirementsabove are satisfied, the refrigerant according to the present disclosurehas a refrigerating capacity ratio of 95% or more relative to R410A anda GWP of 100 or less, undergoes fewer or no changes such aspolymerization or decomposition, and also has excellent stability.

The refrigerant D according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), R32, and R1234yf based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), R32, andR1234yf is 100 mass % are within the range of a figure surrounded byline segments gh, hk, and kg that connect the following 3 points:

point g (77.5, 6.9, 15.6),

point h (61.8, 14.6, 23.6), and

point k (77.5, 14.6, 7.9),

or on these line segments;

the line segment gh is represented by coordinates(0.02y²−2.4583y+93.396, y, −0.02y²+1.4583y+6.604); and

the line segments hk and kg are straight lines. When the requirementsabove are satisfied, the refrigerant according to the present disclosurehas a refrigerating capacity ratio of 95% or more relative to R410A anda GWP of 100 or less, undergoes fewer or no changes such aspolymerization or decomposition, and also has excellent stability.

The refrigerant D according to the present disclosure may furthercomprise other additional refrigerants in addition to HFO-1132(E), R32,and R1234yf, as long as the above properties and effects are notimpaired. In this respect, the refrigerant according to the presentdisclosure preferably comprises HFO-1132(E), R32, and R1234yf in a totalamount of 99.5 mass % or more, more preferably 99.75 mass % or more, andstill more preferably 99.9 mass % or more based on the entirerefrigerant.

Such additional refrigerants are not limited, and can be selected from awide range of refrigerants. The mixed refrigerant may comprise a singleadditional refrigerant, or two or more additional refrigerants.

(Examples of Refrigerant D)

The present disclosure is described in more detail below with referenceto Examples of refrigerant D. However, the refrigerant D is not limitedto the Examples.

The composition of each mixed refrigerant of HFO-1132(E), R32, andR1234yf was defined as WCF. A leak simulation was performed using theNIST Standard Reference Database REFLEAK Version 4.0 under theconditions of Equipment, Storage, Shipping, Leak, and Recharge accordingto the ASHRAE Standard 34-2013. The most flammable fraction was definedas WCFF.

A burning velocity test was performed using the apparatus shown in FIG.1 in the following manner. First, the mixed refrigerants used had apurity of 99.5% or more, and were degassed by repeating a cycle offreezing, pumping, and thawing until no traces of air were observed onthe vacuum gauge. The burning velocity was measured by the closedmethod. The initial temperature was ambient temperature. Ignition wasperformed by generating an electric spark between the electrodes in thecenter of a sample cell. The duration of the discharge was 1.0 to 9.9ms, and the ignition energy was typically about 0.1 to 1.0 J. The spreadof the flame was visualized using schlieren photographs. A cylindricalcontainer (inner diameter: 155 mm, length: 198 mm) equipped with twolight transmission acrylic windows was used as the sample cell, and axenon lamp was used as the light source. Schlieren images of the flamewere recorded by a high-speed digital video camera at a frame rate of600 fps and stored on a PC. Tables 113 to 115 show the results.

TABLE 113 Comparative Example Example Example Example 13 Example 12Example 14 Example 16 Item Unit I 11 J 13 K 15 L WCF HFO-1132 (E) Mass %72 57.2 48.5 41.2 35.6 32 28.9 R32 Mass % 0 10 18.3 27.6 36.8 44.2 51.7R1234yf Mass % 28 32.8 33.2 31.2 27.6 23.8 19.4 Burning Velocity cm/s 1010 10 10 10 10 10 (WCF)

TABLE 114 Comparative Example Example Example 14 Example 19 Example 21Example Item Unit M 18 W 20 N 22 WCF HFO-1132 (E) Mass % 52.6 39.2 32.429.3 27.7 24.6 R32 Mass % 0.0 5.0 10.0 14.5 18.2 27.6 R1234yf Mass %47.4 55.8 57.6 56.2 54.1 47.8 Leak condition that results Storage,Storage, Storage, Storage, Storage, Storage, in WCFF Shipping, −40°Shipping, −40° Shipping, −40° Shipping, −40° Shipping, −40° Shipping,−40° C., 0% release, C., 0% release, C., 0% release, C., 0% release, C.,0% release, C., 0% release, on the gas on the gas on the gas on the gason the gas on the gas phase side phase side phase side phase side phaseside phase side WCF HFO-1132 (E) Mass % 72.0 57.8 48.7 43.6 40.6 34.9R32 Mass % 0.0 9.5 17.9 24.2 28.7 38.1 R1234yf Mass % 28.0 32.7 33.432.2 30.7 27.0 Burning Velocity cm/s 8 or less 8 or less 8 or less 8 orless 8 or less 8 or less (WCF) Burning Velocity cm/s 10 10 10   10  10   10   (WCFF)

TABLE 115 Example 23 Example 25 Item Unit O Example 24 P WCF HFO-1132(E) Mass % 22.6 21.2 20.5 HFO-1123 Mass % 36.8 44.2 51.7 R1234yf Mass %40.6 34.6 27.8 Leak condition that results in WCFF Storage, Storage,Storage, Shipping, −40° C., Shipping, −40° C., Shipping, −40° C., 0%release, on 0% release, on 0% release, on the gas phase side the gasphase side the gas phase side WCFF HFO-1132 (E) Mass % 31.4 29.2 27.1HFO-1123 Mass % 45.7 51.1 56.4 R1234yf Mass % 23.0 19.7 16.5 BurningVelocity (WCF) cm/s 8 or less 8 or less 8 or less Burning Velocity(WCFF) cm/s 10   10   10  

The results indicate that under the condition that the mass % ofHFO-1132(E), R32, and R1234yf based on their sum is respectivelyrepresented by x, y, and z, when coordinates (x,y,z) in the ternarycomposition diagram shown in FIG. 14 in which the sum of HFO-1132(E),R32, and R1234yf is 100 mass % are on the line segment that connectspoint I, point J, point K, and point L, or below these line segments,the refrigerant has a WCF lower flammability.

The results also indicate that when coordinates (x,y,z) in the ternarycomposition diagram shown in FIG. 14 are on the line segments thatconnect point M, point M′, point W, point J, point N, and point P, orbelow these line segments, the refrigerant has an ASHRAE lowerflammability.

Mixed refrigerants were prepared by mixing HFO-1132(E), R32, and R1234yfin amounts (mass %) shown in Tables 116 to 144 based on the sum ofFO-1132(E), R32, and R1234yf. The coefficient of performance (COP) ratioand the refrigerating capacity ratio relative to R410 of the mixedrefrigerants shown in Tables 116 to 144 were determined. The conditionsfor calculation were as described below.

Evaporating temperature: 5° C.

Condensation temperature: 45° C.

Degree of superheating: 5 K

Degree of subcooling: 5 K

Compressor efficiency: 70%

Tables 116 to 144 show these values together with the GWP of each mixedrefrigerant.

TABLE 116 Comparative Comparative Comparative Comparative ComparativeComparative Comparative Example 2 Example 3 Example 4 Example 5 Example6 Example 7 Item Unit Example 1 A B A′ B′ A″ B″ HFO-1132(E) Mass % R410A81.6 0.0 63.1 0.0 48.2 0.0 R32 Mass % 18.4 18.1 36.9 36.7 51.8 51.5R1234yf Mass % 0.0 81.9 0.0 63.3 0.0 48.5 GWP — 2088 125 125 250 250 350350 COP Ratio % (relative 100 98.7 103.6 98.7 102.3 99.2 102.2 to R410A)Refrigerating % (relative 100 105.3 62.5 109.9 77.5 112.1 87.3 CapacityRatio to R410A)

TABLE 117 Comparative Comparative Example Example Example 8 ComparativeExample 10 Example 2 Example 4 Item Unit C Example 9 C′ 1 R 3 THFO-1132(E) Mass % 85.5 66.1 52.1 37.8 25.5 16.6 8.6 R32 Mass % 0.0 10.018.2 27.6 36.8 44.2 51.6 R1234yf Mass % 14.5 23.9 29.7 34.6 37.7 39.239.8 GWP — 1 69 125 188 250 300 350 COP Ratio % (relative 99.8 99.3 99.399.6 100.2 100.8 101.4 to R410A) Refrigerating % (relative 92.5 92.592.5 92.5 92.5 92.5 92.5 Capacity Ratio to R410A)

TABLE 118 Comparative Example Example Comparative Example Example 11Example 6 Example 8 Example 12 Example 10 Item Unit E 5 N 7 U G 9 VHFO-1132(E) Mass % 58.3 40.5 27.7 14.9 3.9 39.6 22.8 11.0 R32 Mass % 0.010.0 18.2 27.6 36.7 0.0 10.0 18.1 R1234yf Mass % 41.7 49.5 54.1 57.559.4 60.4 67.2 70.9 GWP — 2 70 125 189 250 3 70 125 COP Ratio %(relative 100.3 100.3 100.7 101.2 101.9 101.4 101.8 102.3 to R410A)Refrigerating % (relative 80.0 80.0 80.0 80.0 80.0 70.0 70.0 70.0Capacity Ratio to R410A)

TABLE 119 Comparative Example Example Example Example Example 13 Example12 Example 14 Example 16 17 Item Unit I 11 J 13 K 15 L Q HFO-1132(E)Mass % 72.0 57.2 48.5 41.2 35.6 32.0 28.9 44.6 R32 Mass % 0.0 10.0 18.327.6 36.8 44.2 51.7 23.0 R1234yf Mass % 28.0 32.8 33.2 31.2 27.6 23.819.4 32.4 GWP — 2 69 125 188 250 300 350 157 COP Ratio % (relative 99.999.5 99.4 99.5 99.6 99.8 100.1 99.4 to R410A) Refrigerating % (relative86.6 88.4 90.9 94.2 97.7 100.5 103.3 92.5 Capacity Ratio to R410A)

TABLE 120 Comparative Example Example Example 14 Example 19 Example 21Example Item Unit M 18 W 20 N 22 HFO-1132(E) Mass % 52.6 39.2 32.4 29.327.7 24.5 R32 Mass % 0.0 5.0 10.0 14.5 18.2 27.6 R1234yf Mass % 47.455.8 57.6 56.2 54.1 47.9 GWP — 2 36 70 100 125 188 COP Ratio % (relative100.5 100.9 100.9 100.8 100.7 100.4 to R410A) Refrigerating % (relative77.1 74.8 75.6 77.8 80.0 85.5 Capacity Ratio to R410A)

TABLE 121 Exam- Exam- Exam- ple 23 Exam- ple 25 ple 26 Item Unit O ple24 P S HFO-1132(E) Mass % 22.6 21.2 20.5 21.9 R32 Mass % 36.8 44.2 51.739.7 R1234yf Mass % 40.6 34.6 27.8 38.4 GWP — 250 300 350 270 COP Ratio% (relative 100.4 100.5 100.6 100.4 to R410A) Refrigerating % (relative91.0 95.0 99.1 92.5 Capacity Ratio to R410A)

TABLE 122 Comparative Comparative Comparative Comparative ExampleExample Comparative Comparative Item Unit Example 15 Example 16 Example17 Example 18 27 28 Example 19 Example 20 HFO-1132(E) Mass % 10.0 20.030.0 40.0 50.0 60.0 70.0 80.0 R32 Mass % 5.0 5.0 5.0 5.0 5.0 5.0 5.0 5.0R1234yf Mass % 85.0 75.0 65.0 55.0 45.0 35.0 25.0 15.0 GWP — 37 37 37 3636 36 35 35 COP Ratio % (relative 103.4 102.6 101.6 100.8 100.2 99.899.6 99.4 to R410A) Refrigerating % (relative 56.4 63.3 69.5 75.2 80.585.4 90.1 94.4 Capacity Ratio to R410A)

TABLE 123 Comparative Comparative Example Comparative ExampleComparative Comparative Comparative Item Unit Example 21 Example 22 29Example 23 30 Example 24 Example 25 Example 26 HFO-1132(E) Mass % 10.020.0 30.0 40.0 50.0 60.0 70.0 80.0 R32 Mass % 10.0 10.0 10.0 10.0 10.010.0 10.0 10.0 R1234yf Mass % 80.0 70.0 60.0 50.0 40.0 30.0 20.0 10.0GWP — 71 71 70 70 70 69 69 69 COP Ratio % (relative 103.1 102.1 101.1100.4 99.8 99.5 99.2 99.1 to R410A) Refrigerating % (relative 61.8 68.374.3 79.7 84.9 89.7 94.2 98.4 Capacity Ratio to R410A)

TABLE 124 Comparative Example Comparative Example Example ComparativeComparative Comparative Item Unit Example 27 31 Example 28 32 33 Example29 Example 30 Example 31 HFO-1132(E) Mass % 10.0 20.0 30.0 40.0 50.060.0 70.0 80.0 R32 Mass % 15.0 15.0 15.0 15.0 15.0 15.0 15.0 15.0R1234yf Mass % 75.0 65.0 55.0 45.0 35.0 25.0 15.0 5.0 GWP — 104 104 104103 103 103 103 102 COP Ratio % (relative 102.7 101.6 100.7 100.0 99.599.2 99.0 98.9 to R410A) Refrigerating % (relative 66.6 72.9 78.6 84.089.0 93.7 98.1 102.2 Capacity Ratio to R410A)

TABLE 125 Comparative Comparative Comparative Comparative ComparativeComparative Comparative Comparative Item Unit Example 32 Example 33Example 34 Example 35 Example 36 Example 37 Example 38 Example 39HFO-1132(E) Mass % 10.0 20.0 30.0 40.0 50.0 60.0 70.0 10.0 R32 Mass %20.0 20.0 20.0 20.0 20.0 20.0 20.0 25.0 R1234yf Mass % 70.0 60.0 50.040.0 30.0 20.0 10.0 65.0 GWP — 138 138 137 137 137 136 136 171 COP Ratio% (relative 102.3 101.2 100.4 99.7 99.3 99.0 98.8 101.9 to R410A)Refrigerating % (relative 71.0 77.1 82.7 88.0 92.9 97.5 101.7 75.0Capacity Ratio to R410A)

TABLE 126 Example Comparative Comparative Comparative ComparativeComparative Comparative Example Item Unit 34 Example 40 Example 41Example 42 Example 43 Example 44 Example 45 35 HFO-1132(E) Mass % 20.030.0 40.0 50.0 60.0 70.0 10.0 20.0 R32 Mass % 25.0 25.0 25.0 25.0 25.025.0 30.0 30.0 R1234yf Mass % 55.0 45.0 35.0 25.0 15.0 5.0 60.0 50.0 GWP— 171 171 171 170 170 170 205 205 COP Ratio % (relative 100.9 100.1 99.699.2 98.9 98.7 101.6 100.7 to R410A) Refrigerating % (relative 81.0 86.691.7 96.5 101.0 105.2 78.9 84.8 Capacity Ratio to R410A)

TABLE 127 Comparative Comparative Comparative Comparative ExampleExample Example Comparative Item Unit Example 46 Example 47 Example 48Example 49 36 37 38 Example 50 HFO-1132(E) Mass % 30.0 40.0 50.0 60.010.0 20.0 30.0 40.0 R32 Mass % 30.0 30.0 30.0 30.0 35.0 35.0 35.0 35.0R1234yf Mass % 40.0 30.0 20.0 10.0 55.0 45.0 35.0 25.0 GWP — 204 204 204204 239 238 238 238 COP Ratio % (relative 100.0 99.5 99.1 98.8 101.4100.6 99.9 99.4 to R410A) Refrigerating % (relative 90.2 95.3 100.0104.4 82.5 88.3 93.7 98.6 Capacity Ratio to R410A)

TABLE 128 Comparative Comparative Comparative Comparative ExampleComparative Comparative Comparative Item Unit Example 51 Example 52Example 53 Example 54 39 Example 55 Example 56 Example 57 HFO-1132(E)Mass % 50.0 60.0 10.0 20.0 30.0 40.0 50.0 10.0 R32 Mass % 35.0 35.0 40.040.0 40.0 40.0 40.0 45.0 R1234yf Mass % 15.0 5.0 50.0 40.0 30.0 20.010.0 45.0 GWP — 237 237 272 272 272 271 271 306 COP Ratio % (relative99.0 98.8 101.3 100.6 99.9 99.4 99.0 101.3 to R410A) Refrigerating %(relative 103.2 107.5 86.0 91.7 96.9 101.8 106.3 89.3 Capacity Ratio toR410A)

TABLE 129 Example Example Comparative Comparative Comparative ExampleComparative Comparative Item Unit 40 41 Example 58 Example 59 Example 6042 Example 61 Example 62 HFO-1132(E) Mass % 20.0 30.0 40.0 50.0 10.020.0 30.0 40.0 R32 Mass % 45.0 45.0 45.0 45.0 50.0 50.0 50.0 50.0R1234yf Mass % 35.0 25.0 15.0 5.0 40.0 30.0 20.0 10.0 GWP — 305 305 305304 339 339 339 338 COP Ratio % (relative 100.6 100.0 99.5 99.1 101.3100.6 100.0 99.5 to R410A) Refrigerating % (relative 94.9 100.0 104.7109.2 92.4 97.8 102.9 107.5 Capacity Ratio to R410A)

TABLE 130 Comparative Comparative Comparative Comparative ExampleExample Example Example Item Unit Example 63 Example 64 Example 65Example 66 43 44 45 46 HFO-1132(E) Mass % 10.0 20.0 30.0 40.0 56.0 59.062.0 65.0 R32 Mass % 55.0 55.0 55.0 55.0 3.0 3.0 3.0 3.0 R1234yf Mass %35.0 25.0 15.0 5.0 41.0 38.0 35.0 32.0 GWP — 373 372 372 372 22 22 22 22COP Ratio % (relative 101.4 100.7 100.1 99.6 100.1 100.0 99.9 99.8 toR410A) Refrigerating % (relative 95.3 100.6 105.6 110.2 81.7 83.2 84.686.0 Capacity Ratio to R410A)

TABLE 131 Example Example Example Example Example Example ExampleExample Item Unit 47 48 49 50 51 52 53 54 HFO-1132(E) Mass % 49.0 52.055.0 58.0 61.0 43.0 46.0 49.0 R32 Mass % 6.0 6.0 6.0 6.0 6.0 9.0 9.0 9.0R1234yf Mass % 45.0 42.0 39.0 36.0 33.0 48.0 45.0 42.0 GWP — 43 43 43 4342 63 63 63 COP Ratio % (relative 100.2 100.0 99.9 99.8 99.7 100.3 100.199.9 to R410A) Refrigerating % (relative 80.9 82.4 83.9 85.4 86.8 80.482.0 83.5 Capacity Ratio to R410A)

TABLE 132 Example Example Example Example Example Example ExampleExample Item Unit 55 56 57 58 59 60 61 62 HFO-1132(E) Mass % 52.0 55.058.0 38.0 41.0 44.0 47.0 50.0 R32 Mass % 9.0 9.0 9.0 12.0 12.0 12.0 12.012.0 R1234yf Mass % 39.0 36.0 33.0 50.0 47.0 44.0 41.0 38.0 GWP — 63 6363 83 83 83 83 83 COP Ratio % (relative 99.8 99.7 99.6 100.3 100.1 100.099.8 99.7 to R410A) Refrigerating % (relative 85.0 86.5 87.9 80.4 82.083.5 85.1 86.6 Capacity Ratio to R410A)

TABLE 133 Example Example Example Example Example Example ExampleExample Item Unit 63 64 65 66 67 68 69 70 HFO-1132(E) Mass % 53.0 33.036.0 39.0 42.0 45.0 48.0 51.0 R32 Mass % 12.0 15.0 15.0 15.0 15.0 15.015.0 15.0 R1234yf Mass % 35.0 52.0 49.0 46.0 43.0 40.0 37.0 34.0 GWP —83 104 104 103 103 103 103 103 COP Ratio % (relative 99.6 100.5 100.3100.1 99.9 99.7 99.6 99.5 to R410A) Refrigerating % (relative 88.0 80.381.9 83.5 85.0 86.5 88.0 89.5 Capacity Ratio to R410A)

TABLE 134 Example Example Example Example Example Example ExampleExample Item Unit 71 72 73 74 75 76 77 78 HFO-1132(E) Mass % 29.0 32.035.0 38.0 41.0 44.0 47.0 36.0 R32 Mass % 18.0 18.0 18.0 18.0 18.0 18.018.0 3.0 R1234yf Mass % 53.0 50.0 47.0 44.0 41.0 38.0 35.0 61.0 GWP —124 124 124 124 124 123 123 23 COP Ratio % (relative 100.6 100.3 100.199.9 99.8 99.6 99.5 101.3 to R410A) Refrigerating % (relative 80.6 82.283.8 85.4 86.9 88.4 89.9 71.0 Capacity Ratio to R410A)

TABLE 135 Example Example Example Example Example Example ExampleExample Item Unit 79 80 81 82 83 84 85 86 HFO-1132(E) Mass % 39.0 42.030.0 33.0 36.0 26.0 29.0 32.0 R32 Mass % 3.0 3.0 6.0 6.0 6.0 9.0 9.0 9.0R1234yf Mass % 58.0 55.0 64.0 61.0 58.0 65.0 62.0 59.0 GWP — 23 23 43 4343 64 64 63 COP Ratio % (relative 101.1 100.9 101.5 101.3 101.0 101.6101.3 101.1 to R410A) Refrigerating % (relative 72.7 74.4 70.5 72.2 73.971.0 72.8 74.5 Capacity Ratio to R410A)

TABLE 136 Example Example Example Example Example Example ExampleExample Item Unit 87 88 89 90 91 92 93 94 HFO-1132(E) Mass % 21.0 24.027.0 30.0 16.0 19.0 22.0 25.0 R32 Mass % 12.0 12.0 12.0 12.0 15.0 15.015.0 15.0 R1234yf Mass % 67.0 64.0 61.0 58.0 69.0 66.0 63.0 60.0 GWP —84 84 84 84 104 104 104 104 COP Ratio % (relative 101.8 101.5 101.2101.0 102.1 101.8 101.4 101.2 to R410A) Refrigerating % (relative 70.872.6 74.3 76.0 70.4 72.3 74.0 75.8 Capacity Ratio to R410A)

TABLE 137 Example Example Example Example Example Example ExampleExample Item Unit 95 96 97 98 99 100 101 102 HFO-1132(E) Mass % 28.012.0 15.0 18.0 21.0 24.0 27.0 25.0 R32 Mass % 15.0 18.0 18.0 18.0 18.018.0 18.0 21.0 R1234yf Mass % 57.0 70.0 67.0 64.0 61.0 58.0 55.0 54.0GWP — 104 124 124 124 124 124 124 144 COP Ratio % (relative 100.9 102.2101.9 101.6 101.3 101.0 100.7 100.7 to R410A) Refrigerating % (relative77.5 70.5 72.4 74.2 76.0 77.7 79.4 80.7 Capacity Ratio to R410A)

TABLE 138 Example Example Example Example Example Example ExampleExample Item Unit 103 104 105 106 107 108 109 110 HFO-1132(E) Mass %21.0 24.0 17.0 20.0 23.0 13.0 16.0 19.0 R32 Mass % 24.0 24.0 27.0 27.027.0 30.0 30.0 30.0 R1234yf Mass % 55.0 52.0 56.0 53.0 50.0 57.0 54.051.0 GWP — 164 164 185 185 184 205 205 205 COP Ratio % (relative 100.9100.6 101.1 100.8 100.6 101.3 101.0 100.8 to R410A) Refrigerating %(relative 80.8 82.5 80.8 82.5 84.2 80.7 82.5 84.2 Capacity Ratio toR410A)

TABLE 139 Example Example Example Example Example Example ExampleExample Item Unit 111 112 113 114 115 116 117 118 HFO-1132(E) Mass %22.0 9.0 12.0 15.0 18.0 21.0 8.0 12.0 R32 Mass % 30.0 33.0 33.0 33.033.0 33.0 36.0 36.0 R1234yf Mass % 48.0 58.0 55.0 52.0 49.0 46.0 56.052.0 GWP — 205 225 225 225 225 225 245 245 COP Ratio % (relative 100.5101.6 101.3 101.0 100.8 100.5 101.6 101.2 to R410A) Refrigerating %(relative 85.9 80.5 82.3 84.1 85.8 87.5 82.0 84.4 Capacity Ratio toR410A)

TABLE 140 Example Example Example Example Example Example ExampleExample Item Unit 119 120 121 122 123 124 125 126 HFO-1132(E) Mass %15.0 18.0 21.0 42.0 39.0 34.0 37.0 30.0 R32 Mass % 36.0 36.0 36.0 25.028.0 31.0 31.0 34.0 R1234yf Mass % 49.0 46.0 43.0 33.0 33.0 35.0 32.036.0 GWP — 245 245 245 170 191 211 211 231 COP Ratio % (relative 101.0100.7 100.5 99.5 99.5 99.8 99.6 99.9 to R410A) Refrigerating % (relative86.2 87.9 89.6 92.7 93.4 93.0 94.5 93.0 Capacity Ratio to R410A)

TABLE 141 Example Example Example Example Example Example ExampleExample Item Unit 127 128 129 130 131 132 133 134 HFO-1132(E) Mass %33.0 36.0 24.0 27.0 30.0 33.0 23.0 26.0 R32 Mass % 34.0 34.0 37.0 37.037.0 37.0 40.0 40.0 R1234yf Mass % 33.0 30.0 39.0 36.0 33.0 30.0 37.034.0 GWP — 231 231 252 251 251 251 272 272 COP Ratio % (relative 99.899.6 100.3 100.1 99.9 99.8 100.4 100.2 to R410A) Refrigerating %(relative 94.5 96.0 91.9 93.4 95.0 96.5 93.3 94.9 Capacity Ratio toR410A)

TABLE 142 Example Example Example Example Example Example ExampleExample Item Unit 135 136 137 138 139 140 141 142 HFO-1132(E) Mass %29.0 32.0 19.0 22.0 25.0 28.0 31.0 18.0 R32 Mass % 40.0 40.0 43.0 43.043.0 43.0 43.0 46.0 R1234yf Mass % 31.0 28.0 38.0 35.0 32.0 29.0 26.036.0 GWP — 272 271 292 292 292 292 292 312 COP Ratio % (relative 100.099.8 100.6 100.4 100.2 100.1 99.9 100.7 to R410A) Refrigerating %(relative 96.4 97.9 93.1 94.7 96.2 97.8 99.3 94.4 Capacity Ratio toR410A)

TABLE 143 Example Example Example Example Example Example ExampleExample Item Unit 143 144 145 146 147 148 149 150 HFO-1132(E) Mass %21.0 23.0 26.0 29.0 13.0 16.0 19.0 22.0 R32 Mass % 46.0 46.0 46.0 46.049.0 49.0 49.0 49.0 R1234yf Mass % 33.0 31.0 28.0 25.0 38.0 35.0 32.029.0 GWP — 312 312 312 312 332 332 332 332 COP Ratio % (relative 100.5100.4 100.2 100.0 101.1 100.9 100.7 100.5 to R410A) Refrigerating %(relative 96.0 97.0 98.6 100.1 93.5 95.1 96.7 98.3 Capacity Ratio toR410A)

TABLE 144 Item Unit Example 151 Example 152 HFO-1132(E) Mass % 25.0 28.0R32 Mass % 49.0 49.0 R1234yf Mass % 26.0 23.0 GWP — 332 332 COP Ratio %(relative 100.3 100.1 to R410A) Refrigerating % (relative 99.8 101.3Capacity Ratio to R410A)

The results also indicate that under the condition that the mass % ofHFO-1132(E), R32, and R1234yf based on their sum is respectivelyrepresented by x, y, and z, when coordinates (x,y,z) in a ternarycomposition diagram in which the sum of HFO-1132(E), R32, and R1234yf is100 mass % are within the range of a figure surrounded by line segmentsIJ, JN, NE, and EI that connect the following 4 points:

point I (72.0, 0.0, 28.0),

point J (48.5, 18.3, 33.2),

point N (27.7, 18.2, 54.1), and

point E (58.3, 0.0, 41.7),

or on these line segments (excluding the points on the line segment EI),

the line segment IJ is represented by coordinates(0.0236y²−1.7616y+72.0, y, −0.0236y²+0.7616y+28.0),

the line segment NE is represented by coordinates (0.012y²−1.9003y+58.3,y, −0.012y²+0.9003y+41.7), and

the line segments JN and EI are straight lines, the refrigerant D has arefrigerating capacity ratio of 80% or more relative to R410A, a GWP of125 or less, and a WCF lower flammability.

The results also indicate that under the condition that the mass % ofHFO-1132(E), R32, and R1234yf based on their sum is respectivelyrepresented by x, y, and z, when coordinates (x,y,z) in a ternarycomposition diagram in which the sum of HFO-1132(E), R32, and R1234yf is100 mass % are within the range of a figure surrounded by line segmentsMM′, M′N, NV, VG, and GM that connect the following 5 points:

point M (52.6, 0.0, 47.4),

point M′ (39.2, 5.0, 55.8),

point N (27.7, 18.2, 54.1),

point V (11.0, 18.1, 70.9), and

point G (39.6, 0.0, 60.4),

or on these line segments (excluding the points on the line segment GM),

the line segment MM′ is represented by coordinates (0.132y²−3.34y+52.6,y, −0.132y²+2.34y+47.4),

the line segment M′N is represented by coordinates(0.0596y²−2.2541y+48.98, y, −0.0596y²+1.2541y+51.02),

the line segment VG is represented by coordinates(0.0123y²−1.8033y+39.6, y, −0.0123y²+0.8033y+60.4), and

the line segments NV and GM are straight lines, the refrigerant Daccording to the present disclosure has a refrigerating capacity ratioof 70% or more relative to R410A, a GWP of 125 or less, and an ASHRAElower flammability.

The results also indicate that under the condition that the mass % ofHFO-1132(E), R32, and R1234yf based on their sum is respectivelyrepresented by x, y, and z, when coordinates (x,y,z) in a ternarycomposition diagram in which the sum of HFO-1132(E), R32, and R1234yf is100 mass % are within the range of a figure surrounded by line segmentsON, NU, and UO that connect the following 3 points:

point O (22.6, 36.8, 40.6),

point N (27.7, 18.2, 54.1), and

point U (3.9, 36.7, 59.4),

or on these line segments,

the line segment ON is represented by coordinates(0.0072y²−0.6701y+37.512, y, −0.0072y²−0.3299y+62.488),

the line segment NU is represented by coordinates(0.0083y²−1.7403y+56.635, y, −0.0083y²+0.7403y+43.365), and

the line segment UO is a straight line, the refrigerant D according tothe present disclosure has a refrigerating capacity ratio of 80% or morerelative to R410A, a GWP of 250 or less, and an ASHRAE lowerflammability.

The results also indicate that under the condition that the mass % ofHFO-1132(E), R32, and R1234yf based on their sum is respectivelyrepresented by x, y, and z, when coordinates (x,y,z) in a ternarycomposition diagram in which the sum of HFO-1132(E), R32, and R1234yf is100 mass % are within the range of a figure surrounded by line segmentsQR, RT, TL, LK, and KQ that connect the following 5 points:

point Q (44.6, 23.0, 32.4),

point R (25.5, 36.8, 37.7),

point T (8.6, 51.6, 39.8),

point L (28.9, 51.7, 19.4), and

point K (35.6, 36.8, 27.6),

or on these line segments,

the line segment QR is represented by coordinates(0.0099y²−1.975y+84.765, y, −0.0099y²+0.975y+15.235),

the line segment RT is represented by coordinates(0.0082y²−1.8683y+83.126, y, −0.0082y²+0.8683y+16.874),

the line segment LK is represented by coordinates(0.0049y²−0.8842y+61.488, y, −0.0049y²−0.1158y+38.512),

the line segment KQ is represented by coordinates(0.0095y²−1.2222y+67.676, y, −0.0095y²+0.2222y+32.324), and

the line segment TL is a straight line, the refrigerant D according tothe present disclosure has a refrigerating capacity ratio of 92.5% ormore relative to R410A, a GWP of 350 or less, and a WCF lowerflammability.

The results further indicate that under the condition that the mass % ofHFO-1132(E), R32, and R1234yf based on their sum is respectivelyrepresented by x, y, and z, when coordinates (x,y,z) in a ternarycomposition diagram in which the sum of HFO-1132(E), R32, and R1234yf is100 mass % are within the range of a figure surrounded by line segmentsPS, ST, and TP that connect the following 3 points:

point P (20.5, 51.7, 27.8),

point S (21.9, 39.7, 38.4), and

point T (8.6, 51.6, 39.8),

or on these line segments,

the line segment PS is represented by coordinates(0.0064y²−0.7103y+40.1, y, −0.0064y²−0.2897y+59.9),

the line segment ST is represented by coordinates(0.0082y²−1.8683y+83.126, y, −0.0082y²+0.8683y+16.874), and

the line segment TP is a straight line, the refrigerant D according tothe present disclosure has a refrigerating capacity ratio of 92.5% ormore relative to R410A, a GWP of 350 or less, and an ASHRAE lowerflammability.

(5-5) Refrigerant E The refrigerant E according to the presentdisclosure is a mixed refrigerant comprising trans-1,2-difluoroethylene(HFO-1132(E)), trifluoroethylene (HFO-1123), and difluoromethane (R32).

The refrigerant E according to the present disclosure has variousproperties that are desirable as an R410A-alternative refrigerant, i.e.,a coefficient of performance equivalent to that of R410A and asufficiently low GWP.

The refrigerant E according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), HFO-1123,and R32 is 100 mass % are within the range of a figure surrounded byline segments IK, KB′, B′H, HR, RG, and GI that connect the following 6points:

point I (72.0, 28.0, 0.0),

point K (48.4, 33.2, 18.4),

point B′ (0.0, 81.6, 18.4),

point H (0.0, 84.2, 15.8),

point R (23.1, 67.4, 9.5), and

point G (38.5, 61.5, 0.0),

or on these line segments (excluding the points on the line segments B′Hand GI);

the line segment IK is represented by coordinates(0.025z²−1.7429z+72.00, −0.025z²+0.7429z+28.0, z),

the line segment HR is represented by coordinates(−0.3123z²+4.234z+11.06, 0.3123z²−5.234z+88.94, z),

the line segment RG is represented by coordinates(−0.0491z²−1.1544z+38.5, 0.0491z²+0.1544z+61.5, z), and

the line segments KB′ and GI are straight lines. When the requirementsabove are satisfied, the refrigerant according to the present disclosurehas WCF lower flammability, a COP ratio of 93% or more relative to thatof R410A, and a GWP of 125 or less.

The refrigerant E according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), HFO-1123,and R32 is 100 mass % are within the range of a figure surrounded byline segments J, JR, RG, and GI that connect the following 4 points:

point I (72.0, 28.0, 0.0),

point J (57.7, 32.8, 9.5),

point R (23.1, 67.4, 9.5), and

point G (38.5, 61.5, 0.0),

or on these line segments (excluding the points on the line segment GI);

the line segment IJ is represented by coordinates (0.025z²−1.7429z+72.0,−0.025z²+0.7429z+28.0, z),

the line segment RG is represented by coordinates(−0.0491z²−1.1544z+38.5, 0.0491z²+0.1544z+61.5, z), and

the line segments JR and GI are straight lines. When the requirementsabove are satisfied, the refrigerant according to the present disclosurehas WCF lower flammability, a COP ratio of 93% or more relative to thatof R410A, and a GWP of 125 or less.

The refrigerant E according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), HFO-1123,and R32 is 100 mass % are within the range of a figure surrounded byline segments MP, PB′, B′H, HR, RG, and GM that connect the following 6points:

point M (47.1, 52.9, 0.0),

point P (31.8, 49.8, 18.4),

point B′ (0.0, 81.6, 18.4),

point H (0.0, 84.2, 15.8),

point R (23.1, 67.4, 9.5), and

point G (38.5, 61.5, 0.0),

or on these line segments (excluding the points on the line segments B′Hand GM);

the line segment MP is represented by coordinates (0.0083z²−0.984z+47.1,−0.0083z²−0.016z+52.9, z),

the line segment HR is represented by coordinates(−0.3123z²+4.234z+11.06, 0.3123z²−5.234z+88.94, z),

the line segment RG is represented by coordinates(−0.0491z²−1.1544z+38.5, 0.0491z²+0.1544z+61.5, z), and

the line segments PB′ and GM are straight lines. When the requirementsabove are satisfied, the refrigerant according to the present disclosurehas ASHRAE lower flammability, a COP ratio of 93% or more relative tothat of R410A, and a GWP of 125 or less.

The refrigerant E according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), HFO-1123,and R32 is 100 mass % are within the range of a figure surrounded byline segments MN, NR, RG, and GM that connect the following 4 points:

point M (47.1, 52.9, 0.0),

point N (38.5, 52.1, 9.5),

point R (23.1, 67.4, 9.5), and

point G (38.5, 61.5, 0.0),

or on these line segments (excluding the points on the line segment GM);

the line segment MN is represented by coordinates (0.0083z²−0.984z+47.1,−0.0083z²−0.016z+52.9, z),

the line segment RG is represented by coordinates(−0.0491z²−1.1544z+38.5, 0.0491z²+0.1544z+61.5, z),

the line segments NR and GM are straight lines. When the requirementsabove are satisfied, the refrigerant according to the present disclosurehas ASHRAE lower flammability, a COP ratio of 93% or more relative tothat of R410A, and a GWP of 65 or less.

The refrigerant E according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), HFO-1123,and R32 is 100 mass % are within the range of a figure surrounded byline segments PS, ST, and TP that connect the following 3 points:

point P (31.8, 49.8, 18.4),

point S (25.4, 56.2, 18.4), and

point T (34.8, 51.0, 14.2),

or on these line segments;

the line segment ST is represented by coordinates(−0.0982z²+0.9622z+40.931, 0.0982z²−1.9622z+59.069, z),

the line segment TP is represented by coordinates (0.0083z²−0.984z+47.1,−0.0083z²−0.016z+52.9, z), and

the line segment PS is a straight line. When the requirements above aresatisfied, the refrigerant according to the present disclosure hasASHRAE lower flammability, a COP ratio of 94.5% or more relative to thatof R410A, and a GWP of 125 or less.

The refrigerant E according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), HFO-1123,and R32 is 100 mass % are within the range of a figure surrounded byline segments QB″, B″D, DU, and UQ that connect the following 4 points:

point Q (28.6, 34.4, 37.0),

point B″ (0.0, 63.0, 37.0),

point D (0.0, 67.0, 33.0), and

point U (28.7, 41.2, 30.1),

or on these line segments (excluding the points on the line segmentB″D);

the line segment DU is represented by coordinates(−3.4962z²+210.71z−3146.1, 3.4962z²−211.71z+3246.1, z),

the line segment UQ is represented by coordinates(0.0135z²−0.9181z+44.133, −0.0135z²−0.0819z+55.867, z), and

the line segments QB″ and B″D are straight lines. When the requirementsabove are satisfied, the refrigerant according to the present disclosurehas ASHRAE lower flammability, a COP ratio of 96% or more relative tothat of R410A, and a GWP of 250 or less.

The refrigerant E according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), HFO-1123,and R32 is 100 mass % are within the range of a figure surrounded byline segments Oc′, c′d′, d′e′, e′a′, and a′O that connect the following5 points:

point O (100.0, 0.0, 0.0),

point c′ (56.7, 43.3, 0.0),

point d′ (52.2, 38.3, 9.5),

point e′ (41.8, 39.8, 18.4), and

point a′ (81.6, 0.0, 18.4),

or on the line segments c′d′, d′e′, and e′a′ (excluding the points c′and a′);

the line segment c′d′ is represented by coordinates(−0.0297z²−0.1915z+56.7, 0.0297z²+1.1915z+43.3, z),

the line segment d′e′ is represented by coordinates(−0.0535z²+0.3229z+53.957, 0.0535z²+0.6771z+46.043, z), and

the line segments Oc′, e′a′, and a′O are straight lines. When therequirements above are satisfied, the refrigerant according to thepresent disclosure has a COP ratio of 92.5% or more relative to that ofR410A, and a GWP of 125 or less.

The refrigerant E according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), HFO-1123,and R32 is 100 mass % are within the range of a figure surrounded byline segments Oc, cd, de, ea′, and a′O that connect the following 5points:

point O (100.0, 0.0, 0.0),

point c (77.7, 22.3, 0.0),

point d (76.3, 14.2, 9.5),

point e (72.2, 9.4, 18.4), and

point a′ (81.6, 0.0, 18.4),

or on the line segments cd, de, and ea′ (excluding the points c and a′);

the line segment cde is represented by coordinates(−0.017z²+0.0148z+77.684, 0.017z²+0.9852z+22.316, z), and

the line segments Oc, ea′, and a′O are straight lines. When therequirements above are satisfied, the refrigerant according to thepresent disclosure has a COP ratio of 95% or more relative to that ofR410A, and a GWP of 125 or less.

The refrigerant E according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), HFO-1123,and R32 is 100 mass % are within the range of a figure surrounded byline segments Oc′, c′d′, d′a, and aO that connect the following 5points:

point O (100.0, 0.0, 0.0),

point c′ (56.7, 43.3, 0.0),

point d′ (52.2, 38.3, 9.5), and

point a (90.5, 0.0, 9.5),

or on the line segments c′d′ and d′a (excluding the points c′ and a);

the line segment c′d′ is represented by coordinates(−0.0297z²−0.1915z+56.7, 0.0297z²+1.1915z+43.3, z), and

the line segments Oc′, d′a, and aO are straight lines. When therequirements above are satisfied, the refrigerant according to thepresent disclosure has a COP ratio of 93.5% or more relative to that ofR410A, and a GWP of 65 or less.

The refrigerant E according to the present disclosure is preferably arefrigerant wherein

when the mass % of HFO-1132(E), HFO-1123, and R32 based on their sum isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), HFO-1123,and R32 is 100 mass % are within the range of a figure surrounded byline segments Oc, cd, da, and aO that connect the following 4 points:

point O (100.0, 0.0, 0.0),

point c (77.7, 22.3, 0.0),

point d (76.3, 14.2, 9.5), and

point a (90.5, 0.0, 9.5),

or on the line segments cd and da (excluding the points c and a);

the line segment cd is represented by coordinates(−0.017z²+0.0148z+77.684, 0.017z²+0.9852z+22.316, z), and

the line segments Oc, da, and aO are straight lines. When therequirements above are satisfied, the refrigerant according to thepresent disclosure has a COP ratio of 95% or more relative to that ofR410A, and a GWP of 65 or less.

The refrigerant E according to the present disclosure may furthercomprise other additional refrigerants in addition to HFO-1132(E),HFO-1123, and R32, as long as the above properties and effects are notimpaired. In this respect, the refrigerant according to the presentdisclosure preferably comprises HFO-1132(E), HFO-1123, and R32 in atotal amount of 99.5 mass % or more, more preferably 99.75 mass % ormore, and even more preferably 99.9 mass % or more, based on the entirerefrigerant.

Such additional refrigerants are not limited, and can be selected from awide range of refrigerants. The mixed refrigerant may comprise a singleadditional refrigerant, or two or more additional refrigerants.

(Examples of Refrigerant E)

The present disclosure is described in more detail below with referenceto Examples of refrigerant E. However, the refrigerant E is not limitedto the Examples.

Mixed refrigerants were prepared by mixing HFO-1132(E), HFO-1123, andR32 at mass % based on their sum shown in Tables 145 and 146.

The composition of each mixture was defined as WCF. A leak simulationwas performed using National Institute of Science and Technology (NIST)Standard Reference Data Base Refleak Version 4.0 under the conditionsfor equipment, storage, shipping, leak, and recharge according to theASHRAE Standard 34-2013. The most flammable fraction was defined asWCFF.

For each mixed refrigerant, the burning velocity was measured accordingto the ANSI/ASHRAE Standard 34-2013. When the burning velocities of theWCF composition and the WCFF composition are 10 cm/s or less, theflammability of such a refrigerant is classified as Class 2L (lowerflammability) in the ASHRAE flammability classification.

A burning velocity test was performed using the apparatus shown in FIG.1 in the following manner. First, the mixed refrigerants used had apurity of 99.5% or more, and were degassed by repeating a cycle offreezing, pumping, and thawing until no traces of air were observed onthe vacuum gauge. The burning velocity was measured by the closedmethod. The initial temperature was ambient temperature. Ignition wasperformed by generating an electric spark between the electrodes in thecenter of a sample cell. The duration of the discharge was 1.0 to 9.9ms, and the ignition energy was typically about 0.1 to 1.0 J. The spreadof the flame was visualized using schlieren photographs. A cylindricalcontainer (inner diameter: 155 mm, length: 198 mm) equipped with twolight transmission acrylic windows was used as the sample cell, and axenon lamp was used as the light source. Schlieren images of the flamewere recorded by a high-speed digital video camera at a frame rate of600 fps and stored on a PC.

Tables 145 and 146 show the results.

TABLE 145 Item Unit I J K L WCF HFO-1132(E) mass % 72.0 57.7 48.4 35.5HFO-1123 mass % 28.0 32.8 33.2 27.5 R32 mass % 0.0 9.5 18.4 37.0 Burningvelocity cm/s 10 10 10 10 (WCF)

TABLE 146 Item Unit M N T P U Q WCF HFO-1132(E) mass % 47.1 38.5 34.831.8 28.7 28.6 HFO-1123 mass % 52.9 52.1 51.0 49.8 41.2 34.4 R32 mass %0.0 9.5 14.2 18.4 30.1 37.0 Leak condition that results Storage,Storage, Storage, Storage, Storage, Storage, in WCFF Shipping, −40°Shipping, −40° Shipping, −40° Shipping, −40° Shipping, −40° Shipping,−40° C., 92%, release, C., 92%, release, C., 92%, release, C., 92%,release, C., 92%, release, C., 92%, release, on the liquid on the liquidon the liquid on the liquid on the liquid on the liquid phase side phaseside phase side phase side phase side phase side WCFF HFO-1132(E) mass %72.0 58.9 51.5 44.6 31.4 27.1 HFO-1123 mass % 28.0 32.4 33.1 32.6 23.218.3 R32 mass % 0.0 8.7 15.4 22.8 45.4 54.6 Burning velocity cm/s 8 orless 8 or less 8 or less 8 or less 8 or less 8 or less (WCF) Burningvelocity cm/s 10 10 10   10   10   10   (WCFF)

The results in Table 1 indicate that in a ternary composition diagram ofa mixed refrigerant of HFO-1132(E), HFO-1123, and R32 in which their sumis 100 mass %, a line segment connecting a point (0.0, 100.0, 0.0) and apoint (0.0, 0.0, 100.0) is the base, the point (0.0, 100.0, 0.0) is onthe left side, and the point (0.0, 0.0, 100.0) is on the right side,when coordinates (x,y,z) are on or below line segments IK and KL thatconnect the following 3 points:

point I (72.0, 28.0, 0.0),

point K (48.4, 33.2, 18.4), and

point L (35.5, 27.5, 37.0);

the line segment IK is represented by coordinates(0.025z²−1.7429z+72.00, −0.025z²+0.7429z+28.00, z), and

the line segment KL is represented by coordinates(0.0098z²−1.238z+67.852, −0.0098z²+0.238z+32.148, z), it can bedetermined that the refrigerant has WCF lower flammability.

For the points on the line segment IK, an approximate curve(x=0.025z²−1.7429z+72.00) was obtained from three points, i.e., I (72.0,28.0, 0.0), J (57.7, 32.8, 9.5), and K (48.4, 33.2, 18.4) by using theleast-square method to determine coordinates (x=0.025z²−1.7429z+72.00,y=100−z−x=−0.00922z²+0.2114z+32.443, z).

Likewise, for the points on the line segment KL, an approximate curvewas determined from three points, i.e., K (48.4, 33.2, 18.4), Example 10(41.1, 31.2, 27.7), and L (35.5, 27.5, 37.0) by using the least-squaremethod to determine coordinates.

The results in Table 146 indicate that in a ternary composition diagramof a mixed refrigerant of HFO-1132(E), HFO-1123, and R32 in which theirsum is 100 mass %, a line segment connecting a point (0.0, 100.0, 0.0)and a point (0.0, 0.0, 100.0) is the base, the point (0.0, 100.0, 0.0)is on the left side, and the point (0.0, 0.0, 100.0) is on the rightside, when coordinates (x,y,z) are on or below line segments MP and PQthat connect the following 3 points:

point M (47.1, 52.9, 0.0),

point P (31.8, 49.8, 18.4), and

point Q (28.6, 34.4, 37.0),

it can be determined that the refrigerant has ASHRAE lower flammability.

In the above, the line segment MP is represented by coordinates(0.0083z²−0.984z+47.1, −0.0083z²−0.016z+52.9, z), and the line segmentPQ is represented by coordinates (0.0135z²−0.9181z+44.133,−0.0135z²−0.0819z+55.867, z).

For the points on the line segment MP, an approximate curve was obtainedfrom three points, i.e., points M, N, and P, by using the least-squaremethod to determine coordinates. For the points on the line segment PQ,an approximate curve was obtained from three points, i.e., points P, U,and Q, by using the least-square method to determine coordinates.

The GWP of compositions each comprising a mixture of R410A(R32=50%/R125=50%) was evaluated based on the values stated in theIntergovernmental Panel on Climate Change (IPCC), fourth report. The GWPof HFO-1132(E), which was not stated therein, was assumed to be 1 fromHFO-1132a (GWP=1 or less) and HFO-1123 (GWP=0.3, described in PatentLiterature 1). The refrigerating capacity of compositions eachcomprising R410A and a mixture of HFO-1132(E) and HFO-1123 wasdetermined by performing theoretical refrigeration cycle calculationsfor the mixed refrigerants using the National Institute of Science andTechnology (NIST) and Reference Fluid Thermodynamic and TransportProperties Database (Refprop 9.0) under the following conditions.

The COP ratio and the refrigerating capacity (which may be referred toas “cooling capacity” or “capacity”) ratio relative to those of R410 ofthe mixed refrigerants were determined. The conditions for calculationwere as described below.

Evaporating temperature: 5° C.

Condensation temperature: 45° C.

Degree of superheating: 5K

Degree of subcooling: 5K

Compressor efficiency: 70%

Tables 147 to 166 show these values together with the GWP of each mixedrefrigerant.

TABLE 147 Comparative Comparative Comparative Comparative ComparativeComparative Comparative Example 2 Example 3 Example 4 Example 5 Example6 Example 7 Item Unit Example 1 A B A′ B′ A″ B″ HFO-1132(E) mass % R410A90.5 0.0 81.6 0.0 63.0 0.0 HFO-1123 mass % 0.0 90.5 0.0 81.6 0.0 63.0R32 mass % 9.5 9.5 18.4 18.4 37.0 37.0 GWP — 2088 65 65 125 125 250 250COP ratio % (relative 100 99.1 92.0 98.7 93.4 98.7 96.1 to R410A)Refrigerating % (relative 100 102.2 111.6 105.3 113.7 110.0 115.4capacity ratio to R410A)

TABLE 148 Comparative Comparative Example Comparative Example 8 Example9 Comparative 1 Example Example 11 Item Unit O C Example 10 U 2 DHFO-1132(E) mass % 100.0 50.0 41.1 28.7 15.2 0.0 HFO-1123 mass % 0.031.6 34.6 41.2 52.7 67.0 R32 mass % 0.0 18.4 24.3 30.1 32.1 33.0 GWP — 1125 165 204 217 228 COP ratio % (relative 99.7 96.0 96.0 96.0 96.0 96.0to R410A) Refrigerating % (relative 98.3 109.9 111.7 113.5 114.8 115.4capacity ratio to R410A)

TABLE 149 Comparative Example Example Comparative Example 12 Comparative3 4 Example 14 Item Unit E Example 13 T S F HFO-1132(E) mass % 53.4 43.434.8 25.4 0.0 HFO-1123 mass % 46.6 47.1 51.0 56.2 74.1 R32 mass % 0.09.5 14.2 18.4 25.9 GWP — 1 65 97 125 176 COP ratio % (relative 94.5 94.594.5 94.5 94.5 to R410A) Refrigerating % (relative 105.6 109.2 110.8112.3 114.8 capacity ratio to R410A)

TABLE 150 Comparative Example Comparative Example 15 Example 6 ExampleExample 16 Item Unit G 5 R 7 H HFO-1132(E) mass % 38.5 31.5 23.1 16.90.0 HFO-1123 mass % 61.5 63.5 67.4 71.1 84.2 R32 mass % 0.0 5.0 9.5 12.015.8 GWP — 1 35 65 82 107 COP ratio % (relative 93.0 93.0 93.0 93.0 93.0to R410A) Refrigerating % (relative 107.0 109.1 110.9 111.9 113.2capacity ratio to R410A)

TABLE 151 Comparative Example Example Comparative Example 17 8 9Comparative Example 19 Item Unit I J K Example 18 L HFO-1132(E) mass %72.0 57.7 48.4 41.1 35.5 HFO-1123 mass % 28.0 32.8 33.2 31.2 27.5 R32mass % 0.0 9.5 18.4 27.7 37.0 GWP — 1 65 125 188 250 COP ratio %(relative 96.6 95.8 95.9 96.4 97.1 to R410A) Refrigerating % (relative103.1 107.4 110.1 112.1 113.2 capacity ratio to R410A)

TABLE 152 Comparative Exam- Exam- Exam- Example 20 ple 10 ple 11 ple 12Item Unit M N P Q HFO-1132(E) mass % 47.1 38.5 31.8 28.6 HFO-1123 mass %52.9 52.1 49.8 34.4 R32 mass % 0.0 9.5 18.4 37.0 GWP — 1 65 125 250 COPratio % (relative 93.9 94.1 94.7 96.9 to R410A) Refrigerating %(relative 106.2 109.7 112.0 114.1 capacity ratio to R410A)

TABLE 153 Comparative Comparative Comparative Example Example ExampleComparative Comparative Item Unit Example 22 Example 23 Example 24 14 1516 Example 25 Example 26 HFO-1132(E) mass % 10.0 20.0 30.0 40.0 50.060.0 70.0 80.0 HFO-1123 mass % 85.0 75.0 65.0 55.0 45.0 35.0 25.0 15.0R32 mass % 5.0 5.0 5.0 5.0 5.0 5.0 5.0 5.0 GWP — 35 35 35 35 35 35 35 35COP ratio % (relative 91.7 92.2 92.9 93.7 94.6 95.6 96.7 97.7 to R410A)Refrigerating % (relative 110.1 109.8 109.2 108.4 107.4 106.1 104.7103.1 capacity ratio to R410A)

TABLE 154 Comparative Comparative Comparative Example Example ExampleComparative Comparative Item Unit Example 27 Example 28 Example 29 17 1819 Example 30 Example 31 HFO-1132(E) mass % 90.0 10.0 20.0 30.0 40.050.0 60.0 70.0 HFO-1123 mass % 5.0 80.0 70.0 60.0 50.0 40.0 30.0 20.0R32 mass % 5.0 10.0 10.0 10.0 10.0 10.0 10.0 10.0 GWP — 35 68 68 68 6868 68 68 COP ratio % (relative 98.8 92.4 92.9 93.5 94.3 95.1 96.1 97.0to R410A) Refrigerating % (relative 101.4 111.7 111.3 110.6 109.6 108.5107.2 105.7 capacity ratio to R410A)

TABLE 155 Comparative Example Example Example Example ExampleComparative Comparative Item Unit Example 32 20 21 22 23 24 Example 33Example 34 HFO-1132(E) mass % 80.0 10.0 20.0 30.0 40.0 50.0 60.0 70.0HFO-1123 mass % 10.0 75.0 65.0 55.0 45.0 35.0 25.0 15.0 R32 mass % 10.015.0 15.0 15.0 15.0 15.0 15.0 15.0 GWP — 68 102 102 102 102 102 102 102COP ratio % (relative 98.0 93.1 93.6 94.2 94.9 95.6 96.5 97.4 to R410A)Refrigerating % (relative 104.1 112.9 112.4 111.6 110.6 109.4 108.1106.6 capacity ratio to R410A)

TABLE 156 Comparative Comparative Comparative Comparative ComparativeComparative Comparative Comparative Item Unit Example 35 Example 36Example 37 Example 38 Example 39 Example 40 Example 41 Example 42HFO-1132(E) mass % 80.0 10.0 20.0 30.0 40.0 50.0 60.0 70.0 HFO-1123 mass% 5.0 70.0 60.0 50.0 40.0 30.0 20.0 10.0 R32 mass % 15.0 20.0 20.0 20.020.0 20.0 20.0 20.0 GWP — 102 136 136 136 136 136 136 136 COP ratio %(relative 98.3 93.9 94.3 94.8 95.4 96.2 97.0 97.8 to R410A)Refrigerating % (relative 105.0 113.8 113.2 112.4 111.4 110.2 108.8107.3 capacity ratio to R410A)

TABLE 157 Comparative Comparative Comparative Comparative ComparativeComparative Comparative Comparative Item Unit Example 43 Example 44Example 45 Example 46 Example 47 Example 48 Example 49 Example 50HFO-1132(E) mass % 10.0 20.0 30.0 40.0 50.0 60.0 70.0 10.0 HFO-1123 mass% 65.0 55.0 45.0 35.0 25.0 15.0 5.0 60.0 R32 mass % 25.0 25.0 25.0 25.025.0 25.0 25.0 30.0 GWP — 170 170 170 170 170 170 170 203 COP ratio %(relative 94.6 94.9 95.4 96.0 96.7 97.4 98.2 95.3 to R410A)Refrigerating % (relative 114.4 113.8 113.0 111.9 110.7 109.4 107.9114.8 capacity ratio to R410A)

TABLE 158 Comparative Comparative Comparative Comparative ComparativeExample Example Comparative Item Unit Example 51 Example 52 Example 53Example 54 Example 55 25 26 Example 56 HFO-1132(E) mass % 20.0 30.0 40.050.0 60.0 10.0 20.0 30.0 HFO-1123 mass % 50.0 40.0 30.0 20.0 10.0 55.045.0 35.0 R32 mass % 30.0 30.0 30.0 30.0 30.0 35.0 35.0 35.0 GWP — 203203 203 203 203 237 237 237 COP ratio % (relative 95.6 96.0 96.6 97.297.9 96.0 96.3 96.6 to R410A) Refrigerating % (relative 114.2 113.4112.4 111.2 109.8 115.1 114.5 113.6 capacity ratio to R410A)

TABLE 159 Comparative Comparative Comparative Comparative ComparativeComparative Comparative Comparative Item Unit Example 57 Example 58Example 59 Example 60 Example 61 Example 62 Example 63 Example 64HFO-1132(E) mass % 40.0 50.0 60.0 10.0 20.0 30.0 40.0 50.0 HFO-1123 mass% 25.0 15.0 5.0 50.0 40.0 30.0 20.0 10.0 R32 mass % 35.0 35.0 35.0 40.040.0 40.0 40.0 40.0 GWP — 237 237 237 271 271 271 271 271 COP ratio %(relative 97.1 97.7 98.3 96.6 96.9 97.2 97.7 98.2 to R410A)Refrigerating % (relative 112.6 111.5 110.2 115.1 114.6 113.8 112.8111.7 capacity ratio to R410A)

TABLE 160 Example Example Example Example Example Example ExampleExample Item Unit 27 28 29 30 31 32 33 34 HFO-1132(E) mass % 38.0 40.042.0 44.0 35.0 37.0 39.0 41.0 HFO-1123 mass % 60.0 58.0 56.0 54.0 61.059.0 57.0 55.0 R32 mass % 2.0 2.0 2.0 2.0 4.0 4.0 4.0 4.0 GWP — 14 14 1414 28 28 28 28 COP ratio % (relative 93.2 93.4 93.6 93.7 93.2 93.3 93.593.7 to R410A) Refrigerating % (relative 107.7 107.5 107.3 107.2 108.6108.4 108.2 108.0 capacity ratio to R410A)

TABLE 161 Example Example Example Example Example Example ExampleExample Item Unit 35 36 37 38 39 40 41 42 HFO-1132(E) mass % 43.0 31.033.0 35.0 37.0 39.0 41.0 27.0 HFO-1123 mass % 53.0 63.0 61.0 59.0 57.055.0 53.0 65.0 R32 mass % 4.0 6.0 6.0 6.0 6.0 6.0 6.0 8.0 GWP — 28 41 4141 41 41 41 55 COP ratio % (relative 93.9 93.1 93.2 93.4 93.6 93.7 93.993.0 to R410A) Refrigerating % (relative 107.8 109.5 109.3 109.1 109.0108.8 108.6 110.3 capacity ratio to R410A)

TABLE 162 Example Example Example Example Example Example ExampleExample Item Unit 43 44 45 46 47 48 49 50 HFO-1132(E) mass % 29.0 31.033.0 35.0 37.0 39.0 32.0 32.0 HFO-1123 mass % 63.0 61.0 59.0 57.0 55.053.0 51.0 50.0 R32 mass % 8.0 8.0 8.0 8.0 8.0 8.0 17.0 18.0 GWP — 55 5555 55 55 55 116 122 COP ratio % (relative 93.2 93.3 93.5 93.6 93.8 94.094.5 94.7 to R410A) Refrigerating % (relative 110.1 110.0 109.8 109.6109.5 109.3 111.8 111.9 capacity ratio to R410A)

TABLE 163 Example Example Example Example Example Example ExampleExample Item Unit 51 52 53 54 55 56 57 58 HFO-1132(E) mass % 30.0 27.021.0 23.0 25.0 27.0 11.0 13.0 HFO-1123 mass % 52.0 42.0 46.0 44.0 42.040.0 54.0 52.0 R32 mass % 18.0 31.0 33.0 33.0 33.0 33.0 35.0 35.0 GWP —122 210 223 223 223 223 237 237 COP ratio % (relative 94.5 96.0 96.096.1 96.2 96.3 96.0 96.0 to R410A) Refrigerating % (relative 112.1 113.7114.3 114.2 114.0 113.8 115.0 114.9 capacity ratio to R410A)

TABLE 164 Example Example Example Example Example Example ExampleExample Item Unit 59 60 61 62 63 64 65 66 HFO-1132(E) mass % 15.0 17.019.0 21.0 23.0 25.0 27.0 11.0 HFO-1123 mass % 50.0 48.0 46.0 44.0 42.040.0 38.0 52.0 R32 mass % 35.0 35.0 35.0 35.0 35.0 35.0 35.0 37.0 GWP —237 237 237 237 237 237 237 250 COP ratio % (relative 96.1 96.2 96.296.3 96.4 96.4 96.5 96.2 to R410A) Refrigerating % (relative 114.8 114.7114.5 114.4 114.2 114.1 113.9 115.1 capacity ratio to R410A)

TABLE 165 Example Example Example Example Example Example ExampleExample Item Unit 67 68 69 70 71 72 73 74 HFO-1132(E) mass % 13.0 15.017.0 15.0 17.0 19.0 21.0 23.0 HFO-1123 mass % 50.0 48.0 46.0 50.0 48.046.0 44.0 42.0 R32 mass % 37.0 37.0 37.0 0.0 0.0 0.0 0.0 0.0 GWP — 250250 250 237 237 237 237 237 COP ratio % (relative 96.3 96.4 96.4 96.196.2 96.2 96.3 96.4 to R410A) Refrigerating % (relative 115.0 114.9114.7 114.8 114.7 114.5 114.4 114.2 capacity ratio to R410A)

TABLE 166 Example Example Example Example Example Example ExampleExample Item Unit 75 76 77 78 79 80 81 82 HFO-1132(E) mass % 25.0 27.011.0 19.0 21.0 23.0 25.0 27.0 HFO-1123 mass % 40.0 38.0 52.0 44.0 42.040.0 38.0 36.0 R32 mass % 0.0 0.0 0.0 37.0 37.0 37.0 37.0 37.0 GWP — 237237 250 250 250 250 250 250 COP ratio % (relative 96.4 96.5 96.2 96.596.5 96.6 96.7 96.8 to R410A) Refrigerating % (relative 114.1 113.9115.1 114.6 114.5 114.3 114.1 114.0 capacity ratio to R410A)

The above results indicate that under the condition that the mass % ofFO-1132(E), HFO-1123, and R32 based on their sum is respectivelyrepresented by x, y, and z, when coordinates (x,y,z) in a ternarycomposition diagram in which the sum of HFO-1132(E), HFO-1123, and R32is 100 mass %, a line segment connecting a point (0.0, 100.0, 0.0) and apoint (0.0, 0.0, 100.0) is the base, and the point (0.0, 100.0, 0.0) ison the left side are within the range of a figure surrounded by linesegments that connect the following 4 points:

point O (100.0, 0.0, 0.0),

point A″ (63.0, 0.0, 37.0),

point B″ (0.0, 63.0, 37.0), and

point (0.0, 100.0, 0.0),

or on these line segments,

the refrigerant has a GWP of 250 or less.

The results also indicate that when coordinates (x,y,z) are within therange of a figure surrounded by line segments that connect the following4 points:

point O (100.0, 0.0, 0.0),

point A′ (81.6, 0.0, 18.4),

point B′ (0.0, 81.6, 18.4), and

point (0.0, 100.0, 0.0),

or on these line segments,

the refrigerant has a GWP of 125 or less.

The results also indicate that when coordinates (x,y,z) are within therange of a figure surrounded by line segments that connect the following4 points:

point O (100.0, 0.0, 0.0),

point A (90.5, 0.0, 9.5),

point B (0.0, 90.5, 9.5), and

point (0.0, 100.0, 0.0),

or on these line segments,

the refrigerant has a GWP of 65 or less.

The results also indicate that when coordinates (x,y,z) are on the leftside of line segments that connect the following 3 points:

point C (50.0, 31.6, 18.4),

point U (28.7, 41.2, 30.1), and

point D (52.2, 38.3, 9.5),

or on these line segments,

the refrigerant has a COP ratio of 96% or more relative to that ofR410A.

In the above, the line segment CU is represented by coordinates(−0.0538z²+0.7888z+53.701, 0.0538z²−1.7888z+46.299, z), and the linesegment UD is represented by coordinates

(−3.4962z²+210.71z−3146.1, 3.4962z²−211.71z+3246.1, z).

The points on the line segment CU are determined from three points,i.e., point C, Comparative Example 10, and point U, by using theleast-square method.

The points on the line segment UD are determined from three points,i.e., point U, Example 2, and point D, by using the least-square method.

The results also indicate that when coordinates (x,y,z) are on the leftside of line segments that connect the following 3 points:

point E (55.2, 44.8, 0.0),

point T (34.8, 51.0, 14.2), and

point F (0.0, 76.7, 23.3),

or on these line segments,

the refrigerant has a COP ratio of 94.5% or more relative to that ofR410A.

In the above, the line segment ET is represented by coordinates(−0.0547z² 0.5327z+53.4, 0.0547z²−0.4673z+46.6, z), and the line segmentTF is represented by coordinates (−0.0982z²+0.9622z+40.931,0.0982z²−1.9622z+59.069, z).

The points on the line segment ET are determined from three points,i.e., point E, Example 2, and point T, by using the least-square method.

The points on the line segment TF are determined from three points,i.e., points T, S, and F, by using the least-square method.

The results also indicate that when coordinates (x,y,z) are on the leftside of line segments that connect the following 3 points:

point G (0.0, 76.7, 23.3),

point R (21.0, 69.5, 9.5), and

point H (0.0, 85.9, 14.1),

or on these line segments,

the refrigerant has a COP ratio of 93% or more relative to that ofR410A.

In the above, the line segment GR is represented by coordinates(−0.0491z²−1.1544z+38.5, 0.0491z²+0.1544z+61.5, z), and the line segmentRH is represented by coordinates

(−0.3123z²+4.234z+11.06, 0.3123z²−5.234z+88.94, z).

The points on the line segment GR are determined from three points,i.e., point G, Example 5, and point R, by using the least-square method.

The points on the line segment RH are determined from three points,i.e., point R, Example 7, and point H, by using the least-square method.

In contrast, as shown in, for example, Comparative Examples 8, 9, 13,15, 17, and 18, when R32 is not contained, the concentrations ofHFO-1132(E) and HFO-1123, which have a double bond, become relativelyhigh; this undesirably leads to deterioration, such as decomposition, orpolymerization in the refrigerant compound.

(6) First Embodiment

An air conditioning apparatus 1 serving as a refrigeration cycleapparatus according to a first embodiment is described below withreference to FIG. 16 which is a schematic configuration diagram of arefrigerant circuit and FIG. 17 which is a schematic control blockconfiguration diagram.

The air conditioning apparatus 1 is an apparatus that controls thecondition of air in a subject space by performing a vapor compressionrefrigeration cycle.

The air conditioning apparatus 1 mainly includes an outdoor unit 20, anindoor unit 30, a liquid-side connection pipe 6 and a gas-sideconnection pipe 5 that connect the outdoor unit 20 and the indoor unit30 to each other, a remote controller (not illustrated) serving as aninput device and an output device, and a controller 7 that controlsoperations of the air conditioning apparatus 1.

The air conditioning apparatus 1 performs a refrigeration cycle in whicha refrigerant enclosed in a refrigerant circuit 10 is compressed, cooledor condensed, decompressed, heated or evaporated, and then compressedagain. In the present embodiment, the refrigerant circuit 10 is filledwith a refrigerant for performing a vapor compression refrigerationcycle. The refrigerant is a mixed refrigerant containing1,2-difluoroethylene, and can use any one of the above-describedrefrigerants A to E. Moreover, the refrigerant circuit 10 is filled witha refrigerator oil together with the mixed refrigerant.

(6-1) Outdoor Unit 20

The outdoor unit 20 is connected to the indoor unit 30 via theliquid-side connection pipe 6 and the gas-side connection pipe 5, andconstitutes a part of the refrigerant circuit 10. The outdoor unit 20mainly includes a compressor 21, a four-way switching valve 22, anoutdoor heat exchanger 23, an outdoor expansion valve 24, an outdoor fan25, a liquid-side shutoff valve 29, and a gas-side shutoff valve 28.

The compressor 21 is a device that compresses the refrigerant with a lowpressure in the refrigeration cycle until the refrigerant becomes ahigh-pressure refrigerant. In this case, a compressor having ahermetically sealed structure in which a compression element (notillustrated) of positive-displacement type, such as rotary type orscroll type, is rotationally driven by a compressor motor is used as thecompressor 21. The compressor motor is for changing the capacity, andhas an operational frequency that can be controlled by an inverter. Thecompressor 21 is provided with an additional accumulator (notillustrated) on the suction side (note that the inner capacity of theadditional accumulator is smaller than each of the inner capacities of alow-pressure receiver, an intermediate-pressure receiver, and ahigh-pressure receiver which are described later, and is preferably lessthan or equal to a half of each of the inner capacities).

The four-way switching valve 22, by switching the connection state, canswitch the state between a cooling operation connection state in whichthe discharge side of the compressor 21 is connected to the outdoor heatexchanger 23 and the suction side of the compressor 21 is connected tothe gas-side shutoff valve 28, and a heating operation connection statein which the discharge side of the compressor 21 is connected to thegas-side shutoff valve 28 and the suction side of the compressor 21 isconnected to the outdoor heat exchanger 23.

The outdoor heat exchanger 23 is a heat exchanger that functions as acondenser for the high-pressure refrigerant in the refrigeration cycleduring cooling operation and that functions as an evaporator for thelow-pressure refrigerant in the refrigeration cycle during heatingoperation.

The outdoor fan 25 sucks outdoor air into the outdoor unit 20, causesthe outdoor air to exchange heat with the refrigerant in the outdoorheat exchanger 23, and then generates an air flow to be discharged tothe outside. The outdoor fan 25 is rotationally driven by an outdoor fanmotor.

The outdoor expansion valve 24 is provided between a liquid-side endportion of the outdoor heat exchanger 23 and the liquid-side shutoffvalve 29. The outdoor expansion valve 24 may be, for example, acapillary tube or a mechanical expansion valve that is used togetherwith a temperature-sensitive tube. Preferably, the outdoor expansionvalve 24 is an electric expansion valve that can control the valveopening degree through control.

The liquid-side shutoff valve 29 is a manual valve disposed in aconnection portion of the outdoor unit 20 with respect to theliquid-side connection pipe 6.

The gas-side shutoff valve 28 is a manual valve disposed in a connectionportion of the outdoor unit 20 with respect to the gas-side connectionpipe 5.

The outdoor unit 20 includes an outdoor-unit control unit 27 thatcontrols operations of respective sections constituting the outdoor unit20. The outdoor-unit control unit 27 includes a microcomputer includinga CPU, a memory, and so forth. The outdoor-unit control unit 27 isconnected to an indoor-unit control unit 34 of each indoor unit 30 via acommunication line, and transmits and receives a control signal and soforth.

The outdoor unit 20 includes, for example, a discharge pressure sensor61, a discharge temperature sensor 62, a suction pressure sensor 63, asuction temperature sensor 64, an outdoor heat-exchange temperaturesensor 65, and an outdoor air temperature sensor 66. Each of the sensorsis electrically connected to the outdoor-unit control unit 27, andtransmits a detection signal to the outdoor-unit control unit 27. Thedischarge pressure sensor 61 detects the pressure of the refrigerantflowing through a discharge pipe that connects the discharge side of thecompressor 21 to one of connecting ports of the four-way switching valve22. The discharge temperature sensor 62 detects the temperature of therefrigerant flowing through the discharge pipe. The suction pressuresensor 63 detects the pressure of the refrigerant flowing through asuction pipe that connects the suction side of the compressor 21 to oneof the connecting ports of the four-way switching valve 22. The suctiontemperature sensor 64 detects the temperature of the refrigerant flowingthrough the suction pipe. The outdoor heat-exchange temperature sensor65 detects the temperature of the refrigerant flowing through the outleton the liquid side of the outdoor heat exchanger 23 opposite to the sideconnected to the four-way switching valve 22. The outdoor airtemperature sensor 66 detects the outdoor air temperature before passingthrough the outdoor heat exchanger 23.

(6-2) Indoor Unit 30

The indoor unit 30 is installed on a wall surface or a ceiling in a roomthat is a subject space. The indoor unit 30 is connected to the outdoorunit 20 via the liquid-side connection pipe 6 and the gas-sideconnection pipe 5, and constitutes a part of the refrigerant circuit 10.

The indoor unit 30 includes an indoor heat exchanger 31 and an indoorfan 32.

The liquid side of the indoor heat exchanger 31 is connected to theliquid-side connection pipe 6, and the gas-side end thereof is connectedto the gas-side connection pipe 5. The indoor heat exchanger 31 is aheat exchanger that functions as an evaporator for the low-pressurerefrigerant in the refrigeration cycle during cooling operation and thatfunctions as a condenser for the high-pressure refrigerant in therefrigeration cycle during heating operation.

The indoor fan 32 sucks indoor air into the indoor unit 30, causes theindoor air to exchange heat with the refrigerant in the indoor heatexchanger 31, and then generates an air flow to be discharged to theoutside. The indoor fan 32 is rotationally driven by an indoor fanmotor.

The indoor unit 30 includes an indoor-unit control unit 34 that controlsoperations of respective sections constituting the indoor unit 30. Theindoor-unit control unit 34 includes a microcomputer including a CPU, amemory, and so forth. The indoor-unit control unit 34 is connected tothe outdoor-unit control unit 27 via a communication line, and transmitsand receives a control signal and so forth.

The indoor unit 30 includes, for example, an indoor liquid-sideheat-exchange temperature sensor 71 and an indoor air temperature sensor72. Each of the sensors is electrically connected to the indoor-unitcontrol unit 34, and transmits a detection signal to the indoor-unitcontrol unit 34. The indoor liquid-side heat-exchange temperature sensor71 detects the temperature of the refrigerant flowing through the outleton the liquid side of the indoor heat exchanger 31 opposite to the sideconnected to the four-way switching valve 22. The indoor air temperaturesensor 72 detects the indoor air temperature before passing through theindoor heat exchanger 31.

(6-3) Details of Controller 7

In the air conditioning apparatus 1, the outdoor-unit control unit 27 isconnected to the indoor-unit control unit 34 via the communication line,thereby constituting the controller 7 that controls operations of theair conditioning apparatus 1.

The controller 7 mainly includes a CPU (central processing unit) and amemory, such as a ROM or a RAM. Various processing and control by thecontroller 7 are provided when respective sections included in theoutdoor-unit control unit 27 and/or the indoor-unit control unit 34function together.

(6-4) Operating Modes

Operating modes are described below.

The operating modes include a cooling operating mode and a heatingoperating mode.

The controller 7 determines whether the operating mode is the coolingoperating mode or the heating operating mode and executes the determinedmode based on an instruction received from the remote controller or thelike.

(6-4-1) Cooling Operating Mode

In the air conditioning apparatus 1, in the cooling operating mode, theconnection state of the four-way switching valve 22 is in the coolingoperation connection state in which the discharge side of the compressor21 is connected to the outdoor heat exchanger 23 and the suction side ofthe compressor 21 is connected to the gas-side shutoff valve 28, and therefrigerant filled in the refrigerant circuit 10 is circulated mainlysequentially in the compressor 21, the outdoor heat exchanger 23, theoutdoor expansion valve 24, and the indoor heat exchanger 31.

More specifically, in the refrigerant circuit 10, when the coolingoperating mode is started, the refrigerant is sucked into the compressor21, compressed, and then discharged.

The compressor 21 performs capacity control in accordance with a coolingload required for the indoor unit 30. The capacity control is notlimited, and, for example, controls the operating frequency of thecompressor 21 such that, when the air conditioning apparatus 1 iscontrolled to cause the indoor air temperature to attain a settemperature, the discharge temperature (the detected temperature of thedischarge temperature sensor 62) becomes a value corresponding to thedifference between the set temperature and the indoor temperature (thedetected temperature of the indoor air temperature sensor 72).

The gas refrigerant discharged from the compressor 21 passes through thefour-way switching valve 22 and flows into the gas-side end of theoutdoor heat exchanger 23.

The gas refrigerant which has flowed into the gas-side end of theoutdoor heat exchanger 23 exchanges heat with outdoor-side air suppliedby the outdoor fan 25, hence is condensed and turns into a liquidrefrigerant in the outdoor heat exchanger 23, and flows out from theliquid-side end of the outdoor heat exchanger 23.

The refrigerant which has flowed out from the liquid-side end of theoutdoor heat exchanger 23 is decompressed when passing through theoutdoor expansion valve 24. The outdoor expansion valve 24 iscontrolled, for example, such that the degree of superheating of therefrigerant to be sucked into the compressor 21 becomes a target valueof a predetermined degree of superheating. In this case, the degree ofsuperheating of the sucked refrigerant of the compressor 21 can beobtained, for example, by subtracting a saturation temperaturecorresponding to a suction pressure (the detected pressure of thesuction pressure sensor 63) from a suction temperature (the detectedtemperature of the suction temperature sensor 64). Note that the methodof controlling the valve opening degree of the outdoor expansion valve24 is not limited, and, for example, control may be performed such thatthe discharge temperature of the refrigerant discharged from thecompressor 21 becomes a predetermined temperature, or the degree ofsuperheating of the refrigerant discharged from the compressor 21satisfies a predetermined condition.

The refrigerant decompressed at the outdoor expansion valve 24 passesthrough the liquid-side shutoff valve 29 and the liquid-side connectionpipe 6, and flows into the indoor unit 30.

The refrigerant which has flowed into the indoor unit 30 flows into theindoor heat exchanger 31; exchanges heat with the indoor air supplied bythe indoor fan 32, hence is evaporated, and turns into a gas refrigerantin the indoor heat exchanger 30; and flows out from the gas-side end ofthe indoor heat exchanger 31. The gas refrigerant which has flowed outfrom the gas-side end of the indoor heat exchanger 31 flows to thegas-side connection pipe 5.

The refrigerant which has flowed through the gas-side connection pipe 5passes through the gas-side shutoff valve 28 and the four-way switchingvalve 22, and is sucked into the compressor 21 again.

(6-4-2) Heating Operating Mode

In the air conditioning apparatus 1, in the heating operating mode, theconnection state of the four-way switching valve 22 is in the heatingoperation connection state in which the discharge side of the compressor21 is connected to the gas-side shutoff valve 28 and the suction side ofthe compressor 21 is connected to the outdoor heat exchanger 23, and therefrigerant filled in the refrigerant circuit 10 is circulated mainlysequentially in the compressor 21, the indoor heat exchanger 31, theoutdoor expansion valve 24, and the outdoor heat exchanger 23.

More specifically, in the refrigerant circuit 10, when the heatingoperating mode is started, the refrigerant is sucked into the compressor21, compressed, and then discharged.

The compressor 21 performs capacity control in accordance with a heatingload required for the indoor unit 30. The capacity control is notlimited, and, for example, controls the operating frequency of thecompressor 21 such that, when the air conditioning apparatus 1 iscontrolled to cause the indoor air temperature to attain a settemperature, the discharge temperature (the detected temperature of thedischarge temperature sensor 62) becomes a value corresponding to thedifference between the set temperature and the indoor temperature (thedetected temperature of the indoor air temperature sensor 72).

The gas refrigerant discharged from the compressor 21 flows through thefour-way switching valve 22 and the gas-side connection pipe 5, and thenflows into the indoor unit 30.

The refrigerant which has flowed into the indoor unit 30 flows into thegas-side end of the indoor heat exchanger 31; exchanges heat with theindoor air supplied by the indoor fan 32, hence is condensed, and turnsinto a refrigerant in a gas-liquid two-phase state or a liquidrefrigerant in the indoor heat exchanger 31; and flows out from theliquid-side end of the indoor heat exchanger 31. The refrigerant whichhas flowed out from the liquid-side end of the indoor heat exchanger 31flows to the liquid-side connection pipe 6.

The refrigerant which has flowed through the liquid-side connection pipe6 flows into the outdoor unit 20, passes through the liquid-side shutoffvalve 29, and is decompressed to a low pressure in the refrigerationcycle at the outdoor expansion valve 24. The outdoor expansion valve 24is controlled, for example, such that the degree of superheating of therefrigerant to be sucked into the compressor 21 becomes a target valueof a predetermined degree of superheating. Note that the method ofcontrolling the valve opening degree of the outdoor expansion valve 24is not limited, and, for example, control may be performed such that thedischarge temperature of the refrigerant discharged from the compressor21 becomes a predetermined temperature, or the degree of superheating ofthe refrigerant discharged from the compressor 21 satisfies apredetermined condition.

The refrigerant decompressed at the outdoor expansion valve 24 flowsinto the liquid-side end of the outdoor heat exchanger 23.

The refrigerant which has flowed in from the liquid-side end of theoutdoor heat exchanger 23 exchanges heat with the outdoor air suppliedby the outdoor fan 25, hence is evaporated and turns into a gasrefrigerant in the outdoor heat exchanger 23, and flows out from thegas-side end of the outdoor heat exchanger 23.

The refrigerant which has flowed out from the gas-side end of theoutdoor heat exchanger 23 passes through the four-way switching valve 22and is sucked into the compressor 21 again.

(6-5) Characteristics of First Embodiment

Since the air conditioning apparatus 1 can perform the refrigerationcycle using the refrigerant containing 1,2-difluoroethylene, the airconditioning apparatus 1 can perform a refrigeration cycle using asmall-GWP refrigerant.

(7) Second Embodiment

An air conditioning apparatus 1 a serving as a refrigeration cycleapparatus according to a second embodiment is described below withreference to FIG. 18 which is a schematic configuration diagram of arefrigerant circuit and FIG. 19 which is a schematic control blockconfiguration diagram. Differences from the air conditioning apparatus 1according to the first embodiment are mainly described below.

(7-1) Schematic Configuration of Air Conditioning Apparatus 1 a

The air conditioning apparatus 1 a differs from the air conditioningapparatus 1 according to the first embodiment in that the outdoor unit20 includes a low-pressure receiver 41.

The low-pressure receiver 41 is a refrigerant container that is providedbetween the suction side of the compressor 21 and one of the connectingports of the four-way switching valve 22 and that can store an excessiverefrigerant in the refrigerant circuit 10 as a liquid refrigerant. Notethat, in the present embodiment, the suction pressure sensor 63 and thesuction temperature sensor 64 are provided to detect, as a subject, therefrigerant flowing between the low-pressure receiver 41 and the suctionside of the compressor 21. Moreover, the compressor 21 is provided withan additional accumulator (not illustrated). The low-pressure receiver41 is connected to the downstream side of the additional accumulator.

(7-2) Cooling Operating Mode

In the air conditioning apparatus 1 a, in the cooling operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the evaporation temperature of therefrigerant in the refrigerant circuit 10 becomes a target evaporationtemperature that is determined in accordance with the difference betweenthe set temperature and the indoor temperature (the detected temperatureof the indoor air temperature sensor 72). The evaporation temperature isnot limited; however, may be recognized as, for example, the saturationtemperature of the refrigerant corresponding to the detected pressure ofthe suction pressure sensor 63.

The gas refrigerant discharged from the compressor 21 flows through thefour-way switching valve 22, the outdoor heat exchanger 23, and theoutdoor expansion valve 24 in that order.

In this case, the valve opening degree of the outdoor expansion valve 24is controlled to satisfy a predetermined condition, for example, suchthat the degree of subcooling of the refrigerant flowing through theliquid-side outlet of the outdoor heat exchanger 23 becomes a targetvalue. The degree of subcooling of the refrigerant flowing through theliquid-side outlet of the outdoor heat exchanger 23 is not limited;however, for example, can be obtained by subtracting the saturationtemperature of the refrigerant corresponding to a high pressure of therefrigerant circuit 10 (the detected pressure of the discharge pressuresensor 61) from the detected temperature of the outdoor heat-exchangetemperature sensor 65. Note that the method of controlling the valveopening degree of the outdoor expansion valve 24 is not limited, and,for example, control may be performed such that the dischargetemperature of the refrigerant discharged from the compressor 21 becomesa predetermined temperature, or the degree of superheating of therefrigerant discharged from the compressor 21 satisfies a predeterminedcondition.

The refrigerant decompressed at the outdoor expansion valve 24 passesthrough the liquid-side shutoff valve 29 and the liquid-side connectionpipe 6, flows into the indoor unit 30, is evaporated in the indoor heatexchanger 31, and flows into the gas-side connection pipe 5. Therefrigerant which has flowed through the gas-side connection pipe 5passes through the gas-side shutoff valve 28, the four-way switchingvalve 22, and the low-pressure receiver 41, and is sucked into thecompressor 21 again. Note that the low-pressure receiver 41 stores, asan excessive refrigerant, the liquid refrigerant which has not beencompletely evaporated in the indoor heat exchanger 31.

(7-3) Heating Operating Mode

In the air conditioning apparatus 1 a, in the heating operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the condensation temperature ofthe refrigerant in the refrigerant circuit 10 becomes a targetcondensation temperature that is determined in accordance with thedifference between the set temperature and the indoor temperature (thedetected temperature of the indoor air temperature sensor 72). Thecondensation temperature is not limited; however, may be recognized as,for example, the saturation temperature of the refrigerant correspondingto the detected pressure of the discharge pressure sensor 61.

The gas refrigerant discharged from the compressor 21 flows through thefour-way switching valve 22 and the gas-side connection pipe 5, thenflows into the gas-side end of the indoor heat exchanger 31 of theindoor unit 30, and is condensed in the indoor heat exchanger 31. Therefrigerant which has flowed out from the liquid-side end of the indoorheat exchanger 31 flows through the liquid-side connection pipe 6, flowsinto the outdoor unit 20, passes through the liquid-side shutoff valve29, and is decompressed to a low pressure in the refrigeration cycle atthe outdoor expansion valve 24. Note that the valve opening degree ofthe outdoor expansion valve 24 is controlled to satisfy a predeterminedcondition, for example, such that the degree of subcooling of therefrigerant flowing through the liquid-side outlet of the indoor heatexchanger 31 becomes a target value. The degree of subcooling of therefrigerant flowing through the liquid-side outlet of the indoor heatexchanger 31 is not limited; however, for example, can be obtained bysubtracting the saturation temperature of the refrigerant correspondingto a high pressure of the refrigerant circuit 10 (the detected pressureof the discharge pressure sensor 61) from the detected temperature ofthe indoor liquid-side heat-exchange temperature sensor 71. Note thatthe method of controlling the valve opening degree of the outdoorexpansion valve 24 is not limited, and, for example, control may beperformed such that the discharge temperature of the refrigerantdischarged from the compressor 21 becomes a predetermined temperature,or the degree of superheating of the refrigerant discharged from thecompressor 21 satisfies a predetermined condition.

The refrigerant decompressed at the outdoor expansion valve 24 isevaporated in the outdoor heat exchanger 23, passes through the four-wayswitching valve 22 and the low-pressure receiver 41, and is sucked intothe compressor 21 again. Note that the low-pressure receiver 41 stores,as an excessive refrigerant, the liquid refrigerant which has not beencompletely evaporated in the outdoor heat exchanger 23.

(7-4) Characteristics of Second Embodiment

Since the air conditioning apparatus 1 a can perform the refrigerationcycle using the refrigerant containing 1,2-difluoroethylene, the airconditioning apparatus 1 a can perform a refrigeration cycle using asmall-GWP refrigerant.

Moreover, since the air conditioning apparatus 1 a is provided with thelow-pressure receiver 41, occurrence of liquid compression is preventedwithout execution of control (control of the outdoor expansion valve 24)to ensure that the degree of superheating of the refrigerant to besucked into the compressor 21 is a predetermined value or more. Owing tothis, the control of the outdoor expansion valve 24 can be control tosufficiently ensure the degree of subcooling of the refrigerant flowingthrough the outlet for the outdoor heat exchanger 23 when functioning asthe condenser (which is similarly applied to the indoor heat exchanger31 when functioning as the condenser).

(8) Third Embodiment

An air conditioning apparatus 1 b serving as a refrigeration cycleapparatus according to a third embodiment is described below withreference to FIG. 20 which is a schematic configuration diagram of arefrigerant circuit and FIG. 21 which is a schematic control blockconfiguration diagram. Differences from the air conditioning apparatus 1a according to the second embodiment are mainly described below.

(8-1) Schematic Configuration of Air Conditioning Apparatus 1 b

The air conditioning apparatus 1 b differs from the air conditioningapparatus 1 a according to the second embodiment in that a plurality ofindoor units are provided in parallel and an indoor expansion valve isprovided on the liquid-refrigerant side of an indoor heat exchanger ineach indoor unit.

The air conditioning apparatus 1 b includes a first indoor unit 30 and asecond indoor unit 35 connected in parallel to each other. Similarly tothe above-described embodiment, the first indoor unit 30 includes afirst indoor heat exchanger 31 and a first indoor fan 32, and a firstindoor expansion valve 33 is provided on the liquid-refrigerant side ofthe first indoor heat exchanger 31. The first indoor expansion valve 33is preferably an electric expansion valve of which the valve openingdegree is adjustable. Similarly to the above-described embodiment, thefirst indoor unit 30 includes a first indoor-unit control unit 34; and afirst indoor liquid-side heat-exchange temperature sensor 71, a firstindoor air temperature sensor 72, and a first indoor gas-sideheat-exchange temperature sensor 73 that are electrically connected tothe first indoor-unit control unit 34. The first indoor liquid-sideheat-exchange temperature sensor 71 detects the temperature of therefrigerant flowing through the outlet on the liquid-refrigerant side ofthe first indoor heat exchanger 31. The first indoor gas-sideheat-exchange temperature sensor 73 detects the temperature of therefrigerant flowing through the outlet on the gas-refrigerant side ofthe first indoor heat exchanger 31. Similarly to the first indoor unit30, the second indoor unit 35 includes a second indoor heat exchanger 36and a second indoor fan 37, and a second indoor expansion valve 38 isprovided on the liquid-refrigerant side of the second indoor heatexchanger 36. The second indoor expansion valve 38 is preferably anelectric expansion valve of which the valve opening degree isadjustable. Similarly to the first indoor unit 30, the second indoorunit 35 includes a second indoor-unit control unit 39, and a secondindoor liquid-side heat-exchange temperature sensor 75, a second indoorair temperature sensor 76, and a second indoor gas-side heat-exchangetemperature sensor 77 that are electrically connected to the secondindoor-unit control unit 39.

The air conditioning apparatus 1 b differs from the air conditioningapparatus 1 a according to the second embodiment in that, in an outdoorunit, the outdoor expansion valve 24 is not provided and a bypass pipe40 having a bypass expansion valve 49 is provided.

The bypass pipe 40 is a refrigerant pipe that connects a refrigerantpipe extending from the outlet on the liquid-refrigerant side of theoutdoor heat exchanger 23 to the liquid-side shutoff valve 29 and arefrigerant pipe extending from one of the connecting ports of thefour-way switching valve 22 to the low-pressure receiver 41 to eachother. The bypass expansion valve 49 is preferably an electric expansionvalve of which the valve opening degree is adjustable. The bypass pipe40 is not limited to one provided with the electric expansion valve ofwhich the opening degree is adjustable, and may be, for example, onehaving a capillary tube and an openable and closable electromagneticvalve.

(8-2) Cooling Operating Mode

In the air conditioning apparatus 1 b, in the cooling operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the evaporation temperature of therefrigerant in the refrigerant circuit 10 becomes a target evaporationtemperature. In this case, the target evaporation temperature ispreferably determined in accordance with one of the indoor units 30 and35 having the largest difference between the set temperature and theindoor temperature (an indoor unit having the largest load). Theevaporation temperature is not limited; however, can be recognized as,for example, the saturation temperature of the refrigerant correspondingto the detected pressure of the suction pressure sensor 63.

The gas refrigerant discharged from the compressor 21 passes through thefour-way switching valve 22 and is condensed in the outdoor heatexchanger 23. The refrigerant which has flowed through the outdoor heatexchanger 23 passes through the liquid-side shutoff valve 29 and theliquid-side connection pipe 6, and is sent to the first indoor unit 30and the second indoor unit 35.

In this case, in the first indoor unit 30, the valve opening degree ofthe first indoor expansion valve 33 is controlled to satisfy apredetermined condition, for example, such that the degree ofsuperheating of the refrigerant flowing through the gas-side outlet ofthe first indoor heat exchanger 31 becomes a target value. The degree ofsuperheating of the refrigerant flowing through the gas-side outlet ofthe first indoor heat exchanger 31 is not limited; however, for example,can be obtained by subtracting the saturation temperature of therefrigerant corresponding to a low pressure of the refrigerant circuit10 (the detected pressure of the suction pressure sensor 63) from thedetected temperature of the first indoor gas-side heat-exchangetemperature sensor 73. Moreover, also for the second indoor expansionvalve 38 of the second indoor unit 35, similarly to the first indoorexpansion valve 33, the valve opening degree of the second indoorexpansion valve 38 is controlled to satisfy a predetermined condition,for example, such that the degree of superheating of the refrigerantflowing through the gas-side outlet of the second indoor heat exchanger36 becomes a target value. The degree of superheating of the refrigerantflowing through the gas-side outlet of the second indoor heat exchanger36 is not limited, however, for example, can be obtained by subtractingthe saturation temperature of the refrigerant corresponding to a lowpressure of the refrigerant circuit 10 (the detected pressure of thesuction pressure sensor 63) from the detected temperature of the secondindoor gas-side heat-exchange temperature sensor 77. Each of the valveopening degrees of the first indoor expansion valve 33 and the secondindoor expansion valve 38 may be controlled to satisfy a predeterminedcondition, for example, such that the degree of superheating of therefrigerant obtained by subtracting the saturation temperature of therefrigerant corresponding to the detected pressure of the suctionpressure sensor 63 from the detected temperature of the suctiontemperature sensor 64. Furthermore, the method of controlling each ofthe valve opening degrees of the first indoor expansion valve 33 and thesecond indoor expansion valve 38 is not limited, and, for example,control may be performed such that the discharge temperature of therefrigerant discharged from the compressor 21 becomes a predeterminedtemperature, or the degree of superheating of the refrigerant dischargedfrom the compressor 21 satisfies a predetermined condition.

The refrigerant decompressed at the first indoor expansion valve 33 isevaporated in the first indoor heat exchanger 31, the refrigerantdecompressed at the second indoor expansion valve 38 is evaporated inthe second indoor heat exchanger 36, and the evaporated refrigerants arejoined. Then, the joined refrigerant flows to the gas-side connectionpipe 5. The refrigerant which has flowed through the gas-side connectionpipe 5 passes through the gas-side shutoff valve 28, the four-wayswitching valve 22, and the low-pressure receiver 41, and is sucked intothe compressor 21 again. Note that the low-pressure receiver 41 stores,as an excessive refrigerant, the liquid refrigerants which have not beencompletely evaporated in the first indoor heat exchanger 31 and thesecond indoor heat exchanger 36. Note that the bypass expansion valve 49of the bypass pipe 40 is controlled to be opened or controlled such thatthe valve opening degree thereof is increased when the predeterminedcondition relating to that the refrigerant amount in the outdoor heatexchanger 23 serving as the condenser is excessive. The control on theopening degree of the bypass expansion valve 49 is not limited; however,for example, when the condensation pressure (for example, the detectedpressure of the discharge pressure sensor 61) is a predetermined valueor more, the control may be of opening the bypass expansion valve 49 orincreasing the opening degree of the bypass expansion valve 49.Alternatively, the control may be of switching the bypass expansionvalve 49 between an open state and a closed state at a predeterminedtime interval to increase the passing flow rate.

(8-3) Heating Operating Mode

In the air conditioning apparatus 1 b, in the heating operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the condensation temperature ofthe refrigerant in the refrigerant circuit 10 becomes a targetcondensation temperature. In this case, the target condensationtemperature is preferably determined in accordance with one of theindoor units 30 and 35 having the largest difference between the settemperature and the indoor temperature (an indoor unit having thelargest load). The condensation temperature is not limited; however, maybe recognized as, for example, the saturation temperature of therefrigerant corresponding to the detected pressure of the dischargepressure sensor 61.

The gas refrigerant discharged from the compressor 21 flows through thefour-way switching valve 22 and the gas-side connection pipe 5; then aportion of the refrigerant flows into the gas-side end of the firstindoor heat exchanger 31 of the first indoor unit 30 and is condensed inthe first indoor heat exchanger 31; and another portion of therefrigerant flows into the gas-side end of the second indoor heatexchanger 36 of the second indoor unit 35 and is condensed in the secondindoor heat exchanger 36.

Note that, the valve opening degree of the first indoor expansion valve33 of the first indoor unit 30 is controlled to satisfy a predeterminedcondition, for example, such that the degree of subcooling of therefrigerant flowing through the liquid side of the first indoor heatexchanger 31 becomes a predetermined target value. Also for the secondindoor expansion valve 38 of the second indoor unit 35, the valveopening degree of the second indoor expansion valve 38 is controlledlikewise to satisfy a predetermined condition, for example, such thatthe degree of subcooling of the refrigerant flowing through the liquidside of the second indoor heat exchanger 36 becomes a predeterminedtarget value. The degree of subcooling of the refrigerant flowingthrough the liquid side of the first indoor heat exchanger 31 can beobtained by subtracting the saturation temperature of the refrigerantcorresponding to a high pressure of the refrigerant circuit 10 (thedetected pressure of the discharge pressure sensor 61) from the detectedtemperature of the first indoor liquid-side heat-exchange temperaturesensor 71. Also, the degree of subcooling of the refrigerant flowingthrough the liquid side of the second indoor heat exchanger 36 may besimilarly obtained by subtracting the saturation temperature of therefrigerant corresponding to a high pressure of the refrigerant circuit10 (the detected pressure of the discharge pressure sensor 61) from thedetected temperature of the second indoor liquid-side heat-exchangetemperature sensor 75.

The refrigerant decompressed at the first indoor expansion valve 33 andthe refrigerant decompressed at the second indoor expansion valve 38 arejoined. The joined refrigerant passes through the liquid-side connectionpipe 6 and the liquid-side shutoff valve 29, then is evaporated in theoutdoor heat exchanger 23, passes through the four-way switching valve22 and the low-pressure receiver 41, and is sucked into the compressor21 again. Note that the low-pressure receiver 41 stores, as an excessiverefrigerant, the liquid refrigerant which has not been completelyevaporated in the outdoor heat exchanger 23. In heating operation,although not limited, the bypass expansion valve 49 of the bypass pipe40 may be maintained in, for example, a full-close state.

(8-4) Characteristics of Third Embodiment

Since the air conditioning apparatus 1 b can perform the refrigerationcycle using the refrigerant containing 1,2-difluoroethylene, the airconditioning apparatus 1 b can perform a refrigeration cycle using asmall-GWP refrigerant.

Moreover, since the air conditioning apparatus 1 b is provided with thelow-pressure receiver 41, liquid compression in the compressor 21 can besuppressed. Furthermore, since superheating control is performed on thefirst indoor expansion valve 33 and the second indoor expansion valve 38during cooling operation and subcooling control is performed on thefirst indoor expansion valve 33 and the second indoor expansion valve 38during heating operation, the capacities of the first indoor heatexchanger 31 and the second indoor heat exchanger 36 are likelysufficiently provided.

(9) Fourth Embodiment

An air conditioning apparatus 1 c serving as a refrigeration cycleapparatus according to a fourth embodiment is described below withreference to FIG. 22 which is a schematic configuration diagram of arefrigerant circuit and FIG. 23 which is a schematic control blockconfiguration diagram. Differences from the air conditioning apparatus 1a according to the second embodiment are mainly described below.

(9-1) Schematic Configuration of Air Conditioning Apparatus 1 c

The air conditioning apparatus 1 c differs from the air conditioningapparatus 1 a according to the second embodiment in that the outdoorunit 20 does not include the low-pressure receiver 41, but includes ahigh-pressure receiver 42 and an outdoor bridge circuit 26.

Moreover, the indoor unit 30 includes an indoor liquid-sideheat-exchange temperature sensor 71 that detects the temperature of therefrigerant flowing through the liquid side of the indoor heat exchanger31, an indoor air temperature sensor 72 that detects the temperature ofindoor air, and an indoor gas-side heat-exchange temperature sensor 73that detects the temperature of the refrigerant flowing through the gasside of the indoor heat exchanger 31.

The outdoor bridge circuit 26 is provided between the liquid side of theoutdoor heat exchanger 23 and the liquid-side shutoff valve 29, and hasfour connection portions and check valves provided between theconnection portions. Refrigerant pipes extending to the high-pressurereceiver 42 are connected to two portions that are included in the fourconnection portions of the outdoor bridge circuit 26 and that are otherthan a portion connected to the liquid side of the outdoor heatexchanger 23 and a portion connected to the liquid-side shutoff valve29. The outdoor expansion valve 24 is provided midway in a refrigerantpipe that is included in the aforementioned refrigerant pipes and thatextends from a gas region of the inner space of the high-pressurereceiver 42.

(9-2) Cooling Operating Mode

In the air conditioning apparatus 1 c, in the cooling operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the evaporation temperature of therefrigerant in the refrigerant circuit 10 becomes a target evaporationtemperature that is determined in accordance with the difference betweenthe set temperature and the indoor temperature (the detected temperatureof the indoor air temperature sensor 72). The evaporation temperature isnot limited; however, may be recognized as, for example, the detectedtemperature of the indoor liquid-side heat-exchange temperature sensor71, or the saturation temperature of the refrigerant corresponding tothe detected pressure of the suction pressure sensor 63.

The gas refrigerant discharged from the compressor 21 passes through thefour-way switching valve 22 and is condensed in the outdoor heatexchanger 23. The refrigerant which has flowed through the outdoor heatexchanger 23 flows into the high-pressure receiver 42 via a portion ofthe outdoor bridge circuit 26. Note that the high-pressure receiver 42stores, as the liquid refrigerant, an excessive refrigerant in therefrigerant circuit 10. The gas refrigerant which has flowed out fromthe gas region of the high-pressure receiver 42 is decompressed in theoutdoor expansion valve 24.

In this case, the valve opening degree of the outdoor expansion valve 24is controlled to satisfy a predetermined condition, for example, suchthat the degree of superheating of the refrigerant flowing through thegas-side outlet of the indoor heat exchanger 31 or the degree ofsuperheating of the refrigerant flowing through the suction side of thecompressor 21 becomes a target value. Although not limited, the degreeof superheating of the refrigerant flowing through the gas-side outletof the indoor heat exchanger 31 may be obtained by subtracting thesaturation temperature of the refrigerant corresponding to a lowpressure of the refrigerant circuit 10 (the detected pressure of thesuction pressure sensor 63) from the detected temperature of the indoorgas-side heat-exchange temperature sensor 73. Alternatively, the degreeof superheating of the refrigerant flowing through the suction side ofthe compressor 21 may be obtained by subtracting the saturationtemperature of the refrigerant corresponding to the detected pressure ofthe suction pressure sensor 63 from the detected temperature of thesuction temperature sensor 64. Note that the method of controlling thevalve opening degree of the outdoor expansion valve 24 is not limited,and, for example, control may be performed such that the dischargetemperature of the refrigerant discharged from the compressor 21 becomesa predetermined temperature, or the degree of superheating of therefrigerant discharged from the compressor 21 satisfies a predeterminedcondition.

The refrigerant decompressed at the outdoor expansion valve 24 passesthrough anther portion of the outdoor bridge circuit 26, passes throughthe liquid-side shutoff valve 29 and the liquid-side connection pipe 6,flows into the indoor unit 30, and is evaporated in the indoor heatexchanger 31. The refrigerant which has flowed through the indoor heatexchanger 31 passes through the gas-side connection pipe 5, the gas-sideshutoff valve 28, and the four-way switching valve 22, and is suckedinto the compressor 21 again.

(9-3) Heating Operating Mode

In the air conditioning apparatus 1 c, in the heating operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the condensation temperature ofthe refrigerant in the refrigerant circuit 10 becomes a targetcondensation temperature that is determined in accordance with thedifference between the set temperature and the indoor temperature (thedetected temperature of the indoor air temperature sensor 72). Thecondensation temperature is not limited; however, may be recognized as,for example, the saturation temperature of the refrigerant correspondingto the detected pressure of the discharge pressure sensor 61.

The gas refrigerant discharged from the compressor 21 flows through thefour-way switching valve 22 and the gas-side connection pipe 5, thenflows into the gas-side end of the indoor heat exchanger 31 of theindoor unit 30, and is condensed in the indoor heat exchanger 31. Therefrigerant which has flowed out from the liquid-side end of the indoorheat exchanger 31 flows through the liquid-side connection pipe 6, flowsinto the outdoor unit 20, passes through the liquid-side shutoff valve29, flows through a portion of the outdoor bridge circuit 26, and flowsinto the high-pressure receiver 42. Note that the high-pressure receiver42 stores, as the liquid refrigerant, an excessive refrigerant in therefrigerant circuit 10. The gas refrigerant which has flowed out fromthe gas region of the high-pressure receiver 42 is decompressed to a lowpressure in the refrigeration cycle at the outdoor expansion valve 24.

Note that the valve opening degree of the outdoor expansion valve 24 iscontrolled to satisfy a predetermined condition, for example, such thatthe degree of superheating of the refrigerant to be sucked by thecompressor 21 becomes a target value. The degree of superheating of therefrigerant flowing through the suction side of the compressor 21 is notlimited; however, for example, can be obtained by subtracting thesaturation temperature of the refrigerant corresponding to the detectedpressure of the suction pressure sensor 63 from the detected temperatureof the suction temperature sensor 64. Note that the method ofcontrolling the valve opening degree of the outdoor expansion valve 24is not limited, and, for example, control may be performed such that thedischarge temperature of the refrigerant discharged from the compressor21 becomes a predetermined temperature, or the degree of superheating ofthe refrigerant discharged from the compressor 21 satisfies apredetermined condition.

The refrigerant decompressed at the outdoor expansion valve 24 flowsthrough another portion of the outdoor bridge circuit 26, is evaporatedin the outdoor heat exchanger 23, passes through the four-way switchingvalve 22, and is sucked into the compressor 21 again.

(9-4) Characteristics of Fourth Embodiment

Since the air conditioning apparatus 1 c can perform the refrigerationcycle using the refrigerant containing 1,2-difluoroethylene, the airconditioning apparatus 1 c can perform a refrigeration cycle using asmall-GWP refrigerant.

Moreover, since the air conditioning apparatus 1 c is provided with thehigh-pressure receiver 42, an excessive refrigerant in the refrigerantcircuit 10 can be stored.

(10) Fifth Embodiment

An air conditioning apparatus 1 d serving as a refrigeration cycleapparatus according to a fifth embodiment is described below withreference to FIG. 24 which is a schematic configuration diagram of arefrigerant circuit and FIG. 25 which is a schematic control blockconfiguration diagram. Differences from the air conditioning apparatus 1c according to the fourth embodiment are mainly described below.

(10-1) Schematic Configuration of Air Conditioning Apparatus 1 d

The air conditioning apparatus 1 d differs from the air conditioningapparatus 1 c according to the fourth embodiment in that a plurality ofindoor units are provided in parallel and an indoor expansion valve isprovided on the liquid-refrigerant side of an indoor heat exchanger ineach indoor unit.

The air conditioning apparatus 1 d includes a first indoor unit 30 and asecond indoor unit 35 connected in parallel to each other. Similarly tothe above-described embodiment, the first indoor unit 30 includes afirst indoor heat exchanger 31 and a first indoor fan 32, and a firstindoor expansion valve 33 is provided on the liquid-refrigerant side ofthe first indoor heat exchanger 31. The first indoor expansion valve 33is preferably an electric expansion valve of which the valve openingdegree is adjustable. Similarly to the above-described embodiment, thefirst indoor unit 30 includes a first indoor-unit control unit 34; and afirst indoor liquid-side heat-exchange temperature sensor 71, a firstindoor air temperature sensor 72, and a first indoor gas-sideheat-exchange temperature sensor 73 that are electrically connected tothe first indoor-unit control unit 34. The first indoor liquid-sideheat-exchange temperature sensor 71 detects the temperature of therefrigerant flowing through the outlet on the liquid-refrigerant side ofthe first indoor heat exchanger 31. The first indoor gas-sideheat-exchange temperature sensor 73 detects the temperature of therefrigerant flowing through the outlet on the gas-refrigerant side ofthe first indoor heat exchanger 31. Similarly to the first indoor unit30, the second indoor unit 35 includes a second indoor heat exchanger 36and a second indoor fan 37, and a second indoor expansion valve 38 isprovided on the liquid-refrigerant side of the second indoor heatexchanger 36. The second indoor expansion valve 38 is preferably anelectric expansion valve of which the valve opening degree isadjustable. Similarly to the first indoor unit 30, the second indoorunit 35 includes a second indoor-unit control unit 39, and a secondindoor liquid-side heat-exchange temperature sensor 75, a second indoorair temperature sensor 76, and a second indoor gas-side heat-exchangetemperature sensor 77 that are electrically connected to the secondindoor-unit control unit 39.

(10-2) Cooling Operating Mode

In the air conditioning apparatus 1 c, in the cooling operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the evaporation temperature of therefrigerant in the refrigerant circuit 10 becomes a target evaporationtemperature. In this case, the target evaporation temperature ispreferably determined in accordance with one of the indoor units 30 and35 having the largest difference between the set temperature and theindoor temperature (an indoor unit having the largest load).

The gas refrigerant discharged from the compressor 21 passes through thefour-way switching valve 22 and is condensed in the outdoor heatexchanger 23. The refrigerant which has flowed through the outdoor heatexchanger 23 flows into the high-pressure receiver 42 via a portion ofthe outdoor bridge circuit 26. Note that the high-pressure receiver 42stores, as the liquid refrigerant, an excessive refrigerant in therefrigerant circuit 10. The gas refrigerant which has flowed out fromthe gas region of the high-pressure receiver 42 is decompressed in theoutdoor expansion valve 24. In this case, during cooling operation, theoutdoor expansion valve 24 is controlled such that, for example, thevalve opening degree becomes a full-open state.

The refrigerant which has passed through the outdoor expansion valve 24passes through anther portion of the outdoor bridge circuit 26, passesthrough the liquid-side shutoff valve 29 and the liquid-side connectionpipe 6, and flows into the first indoor unit 30 and the second indoorunit 35.

The refrigerant which has flowed into the first indoor unit 30 isdecompressed at the first indoor expansion valve 33. The valve openingdegree of the first indoor expansion valve 33 is controlled to satisfy apredetermined condition, for example, such that the degree ofsuperheating of the refrigerant flowing through the gas-side outlet ofthe first indoor heat exchanger 31 becomes a target value. Although notlimited, the degree of superheating of the refrigerant flowing throughthe gas-side outlet of the first indoor heat exchanger 31 may beobtained by subtracting the saturation temperature of the refrigerantcorresponding to a low pressure of the refrigerant circuit 10 (thedetected pressure of the suction pressure sensor 63) from the detectedtemperature of the first indoor gas-side heat-exchange temperaturesensor 73. Likewise, the refrigerant which has flowed into the secondindoor unit 35 is decompressed at the second indoor expansion valve 38.The valve opening degree of the second indoor expansion valve 38 iscontrolled to satisfy a predetermined condition, for example, such thatthe degree of superheating of the refrigerant flowing through thegas-side outlet of the second indoor heat exchanger 36 becomes a targetvalue. Although not limited, for example, the degree of superheating ofthe refrigerant flowing through the gas-side outlet of the second indoorheat exchanger 36 may be obtained by subtracting the saturationtemperature of the refrigerant corresponding to a low pressure of therefrigerant circuit 10 (the detected pressure of the suction pressuresensor 63) from the detected temperature of the second indoor gas-sideheat-exchange temperature sensor 77. Each of the valve opening degreesof the first indoor expansion valve 33 and the second indoor expansionvalve 38 may be controlled to satisfy a predetermined condition, forexample, such that the degree of superheating of the refrigerantobtained by subtracting the saturation temperature of the refrigerantcorresponding to the detected pressure of the suction pressure sensor 63from the detected temperature of the suction temperature sensor 64.Furthermore, the method of controlling each of the valve opening degreesof the first indoor expansion valve 33 and the second indoor expansionvalve 38 is not limited, and, for example, control may be performed suchthat the discharge temperature of the refrigerant discharged from thecompressor 21 becomes a predetermined temperature, or the degree ofsuperheating of the refrigerant discharged from the compressor 21satisfies a predetermined condition.

The refrigerant evaporated in the first indoor heat exchanger 31 and therefrigerant evaporated in the second indoor heat exchanger 36 arejoined. Then, the joined refrigerant passes through the gas-sideconnection pipe 5, the gas-side shutoff valve 28, and the four-wayswitching valve 22, and is sucked into the compressor 21 again.

(10-3) Heating Operating Mode

In the air conditioning apparatus 1 c, in the heating operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the condensation temperature ofthe refrigerant in the refrigerant circuit 10 becomes a targetcondensation temperature. In this case, the target condensationtemperature is preferably determined in accordance with one of theindoor units 30 and 35 having the largest difference between the settemperature and the indoor temperature (an indoor unit having thelargest load). The condensation temperature is not limited; however, maybe recognized as, for example, the saturation temperature of therefrigerant corresponding to the detected pressure of the dischargepressure sensor 61.

The gas refrigerant discharged from the compressor 21 flows through thefour-way switching valve 22 and the gas-side connection pipe 5, and thenflows into each of the first indoor unit 30 and the second indoor unit35.

The gas refrigerant which has flowed into the first indoor heatexchanger 31 of the first indoor unit 30 is condensed in the firstindoor heat exchanger 31. The refrigerant which has flowed through thefirst indoor heat exchanger 31 is decompressed at the first indoorexpansion valve 33. The valve opening degree of the first indoorexpansion valve 33 is controlled to satisfy a predetermined condition,for example, such that the degree of subcooling of the refrigerantflowing through the liquid-side outlet of the first indoor heatexchanger 31 becomes a target value. The degree of subcooling of therefrigerant flowing through the liquid-side outlet of the first indoorheat exchanger 31 can be obtained, for example, by subtracting thesaturation temperature of the refrigerant corresponding to the detectedpressure of the discharge pressure sensor 61 from the detectedtemperature of the first indoor liquid-side heat-exchange temperaturesensor 71.

The gas refrigerant which has flowed into the second indoor heatexchanger 36 of the second indoor unit 35 is condensed in the secondindoor heat exchanger 36 likewise. The refrigerant which has flowedthrough the second indoor heat exchanger 36 is decompressed at thesecond indoor expansion valve 38. The valve opening degree of the secondindoor expansion valve 38 is controlled to satisfy a predeterminedcondition, for example, such that the degree of subcooling of therefrigerant flowing through the liquid-side outlet of the second indoorheat exchanger 36 becomes a target value. The degree of subcooling ofthe refrigerant flowing through the liquid-side outlet of the secondindoor heat exchanger 36 can be obtained, for example, by subtractingthe saturation temperature of the refrigerant corresponding to thedetected pressure of the discharge pressure sensor 61 from the detectedtemperature of the second indoor liquid-side heat-exchange temperaturesensor 75.

The refrigerant which has flowed out from the liquid-side end of thefirst indoor heat exchanger 31 and the refrigerant which has flowed outfrom the liquid-side end of the second indoor heat exchanger 36 arejoined. Then, the joined refrigerant passes through the liquid-sideconnection pipe 6 and flows into the outdoor unit 20.

The refrigerant which has flowed into the outdoor unit 20 passes throughthe liquid-side shutoff valve 29, flows through a portion of the outdoorbridge circuit 26, and flows into the high-pressure receiver 42. Notethat the high-pressure receiver 42 stores, as the liquid refrigerant, anexcessive refrigerant in the refrigerant circuit 10. The gas refrigerantwhich has flowed out from the gas region of the high-pressure receiver42 is decompressed to a low pressure in the refrigeration cycle at theoutdoor expansion valve 24. That is, during heating operation, thehigh-pressure receiver 42 stores a pseudo-intermediate-pressurerefrigerant.

Note that the valve opening degree of the outdoor expansion valve 24 iscontrolled to satisfy a predetermined condition, for example, such thatthe degree of superheating of the refrigerant to be sucked by thecompressor 21 becomes a target value. The degree of superheating of therefrigerant to be sucked by the compressor 21 is not limited however,for example, can be obtained by subtracting the saturation temperatureof the refrigerant corresponding to the detected pressure of the suctionpressure sensor 63 from the detected temperature of the suctiontemperature sensor 64. Note that the method of controlling the valveopening degree of the outdoor expansion valve 24 is not limited, and,for example, control may be performed such that the dischargetemperature of the refrigerant discharged from the compressor 21 becomesa predetermined temperature, or the degree of superheating of therefrigerant discharged from the compressor 21 satisfies a predeterminedcondition.

The refrigerant decompressed at the outdoor expansion valve 24 flowsthrough another portion of the outdoor bridge circuit 26, is evaporatedin the outdoor heat exchanger 23, passes through the four-way switchingvalve 22, and is sucked into the compressor 21 again.

(10-4) Characteristics of Fifth Embodiment

Since the air conditioning apparatus 1 d can perform the refrigerationcycle using the refrigerant containing 1,2-difluoroethylene, the airconditioning apparatus 1 d can perform a refrigeration cycle using asmall-GWP refrigerant.

Moreover, since the air conditioning apparatus 1 d is provided with thehigh-pressure receiver 42, an excessive refrigerant in the refrigerantcircuit 10 can be stored.

During heating operation, since superheating control is performed on thevalve opening degree of the outdoor expansion valve 24 to ensurereliability of the compressor 21. Thus, subcooling control can beperformed on the first indoor expansion valve 33 and the second indoorexpansion valve 38 to sufficiently provide the capacities of the firstindoor heat exchanger 31 and the second indoor heat exchanger 36.

(11) Sixth Embodiment

An air conditioning apparatus 1 e serving as a refrigeration cycleapparatus according to a sixth embodiment is described below withreference to FIG. 26 which is a schematic configuration diagram of arefrigerant circuit and FIG. 27 which is a schematic control blockconfiguration diagram. Differences from the air conditioning apparatus 1a according to the second embodiment are mainly described below.

(11-1) Schematic Configuration of Air Conditioning Apparatus 1 e

The air conditioning apparatus 1 e differs from the air conditioningapparatus 1 a according to the second embodiment in that the outdoorunit 20 does not include the low-pressure receiver 41, but includes anintermediate-pressure receiver 43 and does not include the outdoorexpansion valve 24, but includes a first outdoor expansion valve 44 anda second outdoor expansion valve 45.

The intermediate-pressure receiver 43 is a refrigerant container that isprovided between the liquid side of the outdoor heat exchanger 23 andthe liquid-side shutoff valve 29 in the refrigerant circuit 10 and thatcan store, as the liquid refrigerant, an excessive refrigerant in therefrigerant circuit 10.

The first outdoor expansion valve 44 is provided midway in a refrigerantpipe extending from the liquid side of the outdoor heat exchanger 23 tothe intermediate-pressure receiver 43. The second outdoor expansionvalve 45 is provided midway in a refrigerant pipe extending from theintermediate-pressure receiver 43 to the liquid-side shutoff valve 29.The first outdoor expansion valve 44 and the second outdoor expansionvalve 45 are each preferably an electric expansion valve of which thevalve opening degree is adjustable.

(11-2) Cooling Operating Mode

In the air conditioning apparatus 1 e, in the cooling operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the evaporation temperature of therefrigerant in the refrigerant circuit 10 becomes a target evaporationtemperature that is determined in accordance with the difference betweenthe set temperature and the indoor temperature (the detected temperatureof the indoor air temperature sensor 72).

The gas refrigerant discharged from the compressor 21 passes through thefour-way switching valve 22 and then is condensed in the outdoor heatexchanger 23. The refrigerant which has flowed through the outdoor heatexchanger 23 is decompressed at the first outdoor expansion valve 44 toan intermediate pressure in the refrigeration cycle.

In this case, the valve opening degree of the first outdoor expansionvalve 44 is controlled to satisfy a predetermined condition, forexample, such that the degree of subcooling of the refrigerant flowingthrough the liquid-side outlet of the outdoor heat exchanger 23 becomesa target value.

The refrigerant decompressed at the first outdoor expansion valve 44flows into the intermediate-pressure receiver 43. Theintermediate-pressure receiver 43 stores, as the liquid refrigerant, anexcessive refrigerant in the refrigerant circuit 10. The refrigerantwhich has passed through the intermediate-pressure receiver 43 isdecompressed to a low pressure in the refrigeration cycle at the secondoutdoor expansion valve 45.

In this case, the valve opening degree of the second outdoor expansionvalve 45 is controlled to satisfy a predetermined condition, forexample, such that the degree of superheating of the refrigerant flowingthrough the gas side of the indoor heat exchanger 31 or the degree ofsuperheating of the refrigerant to be sucked by the compressor 21becomes a target value. Note that the method of controlling the valveopening degree of the second outdoor expansion valve 45 is not limited,and, for example, control may be performed such that the dischargetemperature of the refrigerant discharged from the compressor 21 becomesa predetermined temperature, or the degree of superheating of therefrigerant discharged from the compressor 21 satisfies a predeterminedcondition.

The refrigerant decompressed at the second outdoor expansion valve 45 tothe low pressure in the refrigeration cycle passes through theliquid-side shutoff valve 29 and the liquid-side connection pipe 6,flows into the indoor unit 30, and is evaporated in the indoor heatexchanger 31. The refrigerant which has flowed through the indoor heatexchanger 31 flows through the gas-side connection pipe 5, then passesthrough the gas-side shutoff valve 28 and the four-way switching valve22, and is sucked into the compressor 21 again.

(11-3) Heating Operating Mode

In the air conditioning apparatus 1 e, in the heating operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the condensation temperature ofthe refrigerant in the refrigerant circuit 10 becomes a targetcondensation temperature that is determined in accordance with thedifference between the set temperature and the indoor temperature (thedetected temperature of the indoor air temperature sensor 72).

The gas refrigerant discharged from the compressor 21 flows through thefour-way switching valve 22 and the gas-side connection pipe 5, thenflows into the gas-side end of the indoor heat exchanger 31 of theindoor unit 30, and is condensed in the indoor heat exchanger 31. Therefrigerant which has flowed out from the liquid-side end of the indoorheat exchanger 31 flows through the liquid-side connection pipe 6, flowsinto the outdoor unit 20, passes through the liquid-side shutoff valve29, and is decompressed to an intermediate pressure in the refrigerationcycle at the second outdoor expansion valve 45.

In this case, the valve opening degree of the second outdoor expansionvalve 45 is controlled to satisfy a predetermined condition, forexample, such that the degree of subcooling of the refrigerant flowingthrough the liquid-side outlet of the indoor heat exchanger 31 becomes atarget value.

The refrigerant decompressed at the second outdoor expansion valve 45flows into the intermediate-pressure receiver 43. Theintermediate-pressure receiver 43 stores, as the liquid refrigerant, anexcessive refrigerant in the refrigerant circuit 10. The refrigerantwhich has passed through the intermediate-pressure receiver 43 isdecompressed to a low pressure in the refrigeration cycle at the firstoutdoor expansion valve 44.

In this case, the valve opening degree of the first outdoor expansionvalve 44 is controlled to satisfy a predetermined condition, forexample, such that the degree of superheating of the refrigerant to besucked by the compressor 21 becomes a target value. Note that the methodof controlling the valve opening degree of the first outdoor expansionvalve 44 is not limited, and, for example, control may be performed suchthat the discharge temperature of the refrigerant discharged from thecompressor 21 becomes a predetermined temperature, or the degree ofsuperheating of the refrigerant discharged from the compressor 21satisfies a predetermined condition.

The refrigerant decompressed at the first outdoor expansion valve 44 isevaporated in the outdoor heat exchanger 23, passes through the four-wayswitching valve 22, and is sucked into the compressor 21 again.

(11-4) Characteristics of Sixth Embodiment

Since the air conditioning apparatus 1 e can perform the refrigerationcycle using the refrigerant containing 1,2-difluoroethylene, the airconditioning apparatus 1 e can perform a refrigeration cycle using asmall-GWP refrigerant.

Moreover, since the air conditioning apparatus 1 e is provided with theintermediate-pressure receiver 43, an excessive refrigerant in therefrigerant circuit 10 can be stored. During cooling operation, sincesubcooling control is performed on the first outdoor expansion valve 44,the capacity of the outdoor heat exchanger 23 can be likely sufficientlyprovided. During heating operation, since subcooling control isperformed on the second outdoor expansion valve 45, the capacity of theindoor heat exchanger 31 can be likely sufficiently provided.

(12) Seventh Embodiment

An air conditioning apparatus 1 f serving as a refrigeration cycleapparatus according to a seventh embodiment is described below withreference to FIG. 28 which is a schematic configuration diagram of arefrigerant circuit and FIG. 29 which is a schematic control blockconfiguration diagram. Differences from the air conditioning apparatus 1e according to the sixth embodiment are mainly described below.

(12-1) Schematic Configuration of Air Conditioning Apparatus 1 f

The air conditioning apparatus 1 f differs from the air conditioningapparatus 1 e according to the sixth embodiment in that the outdoor unit20 includes a first outdoor heat exchanger 23 a and a second outdoorheat exchanger 23 b disposed in parallel to each other, includes a firstbranch outdoor expansion valve 24 a on the liquid-refrigerant side ofthe first outdoor heat exchanger 23 a, and includes a second branchoutdoor expansion valve 24 b on the liquid-refrigerant side of thesecond outdoor heat exchanger 23 b. The first branch outdoor expansionvalve 24 a and the second branch outdoor expansion valve 24 b are eachpreferably an electric expansion valve of which the valve opening degreeis adjustable.

Moreover, the air conditioning apparatus 1 f differs from the airconditioning apparatus 1 e according to the sixth embodiment in that aplurality of indoor units are provided in parallel and an indoorexpansion valve is provided on the liquid-refrigerant side of an indoorheat exchanger in each indoor unit.

The air conditioning apparatus 1 f includes a first indoor unit 30 and asecond indoor unit 35 connected in parallel to each other. Similarly tothe above-described embodiment, the first indoor unit 30 includes afirst indoor heat exchanger 31 and a first indoor fan 32, and a firstindoor expansion valve 33 is provided on the liquid-refrigerant side ofthe first indoor heat exchanger 31. The first indoor expansion valve 33is preferably an electric expansion valve of which the valve openingdegree is adjustable. Similarly to the above-described embodiment, thefirst indoor unit 30 includes a first indoor-unit control unit 34, and afirst indoor liquid-side heat-exchange temperature sensor 71, a firstindoor air temperature sensor 72, and a first indoor gas-sideheat-exchange temperature sensor 73 that are electrically connected tothe first indoor-unit control unit 34. The first indoor liquid-sideheat-exchange temperature sensor 71 detects the temperature of therefrigerant flowing through the outlet on the liquid-refrigerant side ofthe first indoor heat exchanger 31. The first indoor gas-sideheat-exchange temperature sensor 73 detects the temperature of therefrigerant flowing through the outlet on the gas-refrigerant side ofthe first indoor heat exchanger 31. Similarly to the first indoor unit30, the second indoor unit 35 includes a second indoor heat exchanger 36and a second indoor fan 37, and a second indoor expansion valve 38 isprovided on the liquid-refrigerant side of the second indoor heatexchanger 36. The second indoor expansion valve 38 is preferably anelectric expansion valve of which the valve opening degree isadjustable. Similarly to the first indoor unit 30, the second indoorunit 35 includes a second indoor-unit control unit 39, and a secondindoor liquid-side heat-exchange temperature sensor 75, a second indoorair temperature sensor 76, and a second indoor gas-side heat-exchangetemperature sensor 77 that are electrically connected to the secondindoor-unit control unit 39.

(12-2) Cooling Operating Mode

In the air conditioning apparatus 1 f, in the cooling operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the evaporation temperature of therefrigerant in the refrigerant circuit 10 becomes a target evaporationtemperature. In this case, the target evaporation temperature ispreferably determined in accordance with one of the indoor units 30 and35 having the largest difference between the set temperature and theindoor temperature (an indoor unit having the largest load).

The gas refrigerant discharged from the compressor 21 passes through thefour-way switching valve 22, then is branched and flows to the firstoutdoor heat exchanger 23 a and the second outdoor heat exchanger 23 b,and the respective branched refrigerants are condensed in the firstoutdoor heat exchanger 23 a and the second outdoor heat exchanger 23 b.The refrigerant which has flowed through the first outdoor heatexchanger 23 a is decompressed at the first branch outdoor expansionvalve 24 a to an intermediate pressure in the refrigeration cycle. Therefrigerant which has flowed through the second outdoor heat exchanger23 b is decompressed at the second branch outdoor expansion valve 24 bto an intermediate pressure in the refrigeration cycle.

In this case, each of the first branch outdoor expansion valve 24 a andthe second branch outdoor expansion valve 24 b may be controlled, forexample, to be in a full-open state.

Moreover, when the first outdoor heat exchanger 23 a and the secondoutdoor heat exchanger 23 b have a difference in easiness of flowing ofthe refrigerant due to the structure thereof or the connection ofrefrigerant pipes, the valve opening degree of the first branch outdoorexpansion valve 24 a may be controlled to satisfy a predeterminedcondition, for example, such that the degree of subcooling of therefrigerant flowing through the liquid-side outlet of the first outdoorheat exchanger 23 a becomes a common target value, and the valve openingdegree of the second branch outdoor expansion valve 24 b may becontrolled to satisfy a predetermined condition, for example, such thatthe degree of subcooling of the refrigerant flowing through theliquid-side outlet of the second outdoor heat exchanger 23 b becomes acommon target value. With the control, an uneven flow of the refrigerantbetween the first outdoor heat exchanger 23 a and the second outdoorheat exchanger 23 b can be minimized.

The refrigerant which has passed through the first branch outdoorexpansion valve 24 a and the refrigerant which has passed through thesecond branch outdoor expansion valve 24 b are joined. Then, the joinedrefrigerant flows into the intermediate-pressure receiver 43. Theintermediate-pressure receiver 43 stores, as the liquid refrigerant, anexcessive refrigerant in the refrigerant circuit 10. The refrigerantwhich has passed through the intermediate-pressure receiver 43 flowsthrough the liquid-side shutoff valve 29 and the liquid-side connectionpipe 6, and flows into each of the first indoor unit 30 and the secondindoor unit 35.

The refrigerant which has flowed into the first indoor unit 30 isdecompressed at the first indoor expansion valve 33 to a low pressure inthe refrigeration cycle. The refrigerant which has flowed into thesecond indoor unit 35 is decompressed at the second indoor expansionvalve 38 to a low pressure in the refrigeration cycle.

In this case, the valve opening degree of the first indoor expansionvalve 33 is controlled to satisfy a predetermined condition, forexample, such that the degree of superheating of the refrigerant flowingthrough the gas side of the first indoor heat exchanger 31 or the degreeof superheating of the refrigerant to be sucked by the compressor 21becomes a target value. Moreover, likewise, the valve opening degree ofthe second indoor expansion valve 38 is also controlled to satisfy apredetermined condition, for example, such that the degree ofsuperheating of the refrigerant flowing through the gas side of thesecond indoor heat exchanger 36 or the degree of superheating of therefrigerant to be sucked by the compressor 21 becomes a target value.Note that the method of controlling each of the valve opening degrees ofthe first indoor expansion valve 33 and the second indoor expansionvalve 38 is not limited, and, for example, control may be performed suchthat the discharge temperature of the refrigerant discharged from thecompressor 21 becomes a predetermined temperature, or the degree ofsuperheating of the refrigerant discharged from the compressor 21satisfies a predetermined condition.

The refrigerant decompressed at the first indoor expansion valve 33 isevaporated in the first indoor heat exchanger 31, the refrigerantdecompressed at the second indoor expansion valve 38 is evaporated inthe second indoor heat exchanger 36, and the evaporated refrigerants arejoined. Then, the joined refrigerant passes through the gas-sideconnection pipe 5, the gas-side shutoff valve 28, and the four-wayswitching valve 22, and is sucked by the compressor 21 again.

(12-3) Heating Operating Mode

In the air conditioning apparatus 1 f, in the heating operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the condensation temperature ofthe refrigerant in the refrigerant circuit 10 becomes a targetcondensation temperature. In this case, the target condensationtemperature is preferably determined in accordance with one of theindoor units 30 and 35 having the largest difference between the settemperature and the indoor temperature (an indoor unit having thelargest load).

The gas refrigerant discharged from the compressor 21 flows through thefour-way switching valve 22 and the gas-side connection pipe 5, and thenflows into each of the first indoor unit 30 and the second indoor unit35.

The refrigerant which has flowed into the first indoor unit 30 iscondensed in the first indoor heat exchanger 31. The refrigerant whichhas flowed into the second indoor unit 35 is condensed in the secondindoor heat exchanger 36.

The refrigerant which has flowed out from the liquid-side end of thefirst indoor heat exchanger 31 is decompressed at the first indoorexpansion valve 33 to an intermediate pressure in the refrigerationcycle. The refrigerant which has flowed out from the second indoor heatexchanger 36 is decompressed at the second indoor expansion valve 38 toan intermediate pressure in the refrigeration cycle.

In this case, the valve opening degree of the first indoor expansionvalve 33 is controlled to satisfy a predetermined condition, forexample, such that the degree of subcooling of the refrigerant flowingthrough the liquid-side outlet of the first indoor heat exchanger 31becomes a target value. Also, the valve opening degree of the secondindoor expansion valve 38 is controlled likewise to satisfy apredetermined condition, for example, such that the degree of subcoolingof the refrigerant flowing through the liquid-side outlet of the secondindoor heat exchanger 36 becomes a target value.

The refrigerant which has passed through the first indoor expansionvalve 33 and the refrigerant which has passed through the second indoorexpansion valve 38 are joined. Then, the joined refrigerant passesthrough the liquid-side connection pipe 6 and flows into the outdoorunit 20.

The refrigerant which has flowed into the outdoor unit 20 passes throughthe liquid-side shutoff valve 29, and is sent to theintermediate-pressure receiver 43. The intermediate-pressure receiver 43stores, as the liquid refrigerant, an excessive refrigerant in therefrigerant circuit 10. The refrigerant which has passed through theintermediate-pressure receiver 43 flows in a separated manner to thefirst branch outdoor expansion valve 24 a and the second branch outdoorexpansion valve 24 b.

The first branch outdoor expansion valve 24 a decompresses the passingrefrigerant to a low pressure in the refrigeration cycle. The secondbranch outdoor expansion valve 24 b similarly decompresses the passingrefrigerant to a low pressure in the refrigeration cycle.

In this case, each of the valve opening degrees of the first branchoutdoor expansion valve 24 a and the second branch outdoor expansionvalve 24 b is controlled to satisfy a predetermined condition, forexample, such that the degree of superheating of the refrigerant to besucked by the compressor 21 becomes a target value. Note that the methodof controlling each of the valve opening degrees of the first branchoutdoor expansion valve 24 a and the second branch outdoor expansionvalve 24 b is not limited, and, for example, control may be performedsuch that the discharge temperature of the refrigerant discharged fromthe compressor 21 becomes a predetermined temperature, or the degree ofsuperheating of the refrigerant discharged from the compressor 21satisfies a predetermined condition.

The refrigerant decompressed at the first branch outdoor expansion valve24 a is evaporated in the first outdoor heat exchanger 23 a, therefrigerant decompressed at the second branch outdoor expansion valve 24b is evaporated in the second outdoor heat exchanger 23 b, and theevaporated refrigerants are joined. Then, the joined refrigerant passesthrough the four-way switching valve 22 and is sucked by the compressor21 again.

(12-4) Characteristics of Seventh Embodiment

Since the air conditioning apparatus 1 f can perform the refrigerationcycle using the refrigerant containing 1,2-difluoroethylene, the airconditioning apparatus 1 f can perform a refrigeration cycle using asmall-GWP refrigerant.

Moreover, since the air conditioning apparatus f is provided with theintermediate-pressure receiver 43, an excessive refrigerant in therefrigerant circuit 10 can be stored. During heating operation, sincesubcooling control is performed on the first indoor expansion valve 33and the second indoor expansion valve 38, the capacity of the indoorheat exchanger 31 can be likely sufficiently provided.

(13) Eighth Embodiment

An air conditioning apparatus 1 g serving as a refrigeration cycleapparatus according to an eighth embodiment is described below withreference to FIG. 30 which is a schematic configuration diagram of arefrigerant circuit and FIG. 31 which is a schematic control blockconfiguration diagram. Differences from the air conditioning apparatus 1b according to the third embodiment are mainly described below.

(13-1) Schematic Configuration of Air Conditioning Apparatus 1 g

The air conditioning apparatus 1 g differs from the air conditioningapparatus 1 b according to the third embodiment in that the bypass pipe40 having the bypass expansion valve 49 is not provided, a subcoolingheat exchanger 47 is provided, a subcooling pipe 46 is provided, a firstoutdoor expansion valve 44 and a second outdoor expansion valve 45 areprovided, and a subcooling temperature sensor 67 is provided.

The first outdoor expansion valve 44 is provided between the liquid-sideoutlet of the outdoor heat exchanger 23 and the liquid-side shutoffvalve 29 in the refrigerant circuit 10. The second outdoor expansionvalve 45 is provided between the first outdoor expansion valve 44 andthe liquid-side shutoff valve 29 in the refrigerant circuit 10. Thefirst outdoor expansion valve 44 and the second outdoor expansion valve45 are each preferably an electric expansion valve of which the valveopening degree is adjustable.

The subcooling pipe 46 is, in the refrigerant circuit 10, branched froma branch portion between the first outdoor expansion valve 44 and thesecond outdoor expansion valve 45, and is joined to a joint portionbetween one of the connecting ports of the four-way switching valve 22and the low-pressure receiver 41. The subcooling pipe 46 is providedwith a subcooling expansion valve 48. The subcooling expansion valve 48is preferably an electric expansion valve of which the valve openingdegree is adjustable.

The subcooling heat exchanger 47 is, in the refrigerant circuit 10, aheat exchanger that causes the refrigerant flowing through the portionbetween the first outdoor expansion valve 44 and the second outdoorexpansion valve 45 and the refrigerant flowing through a portion on thejoint portion side of the subcooling expansion valve 48 in thesubcooling pipe 46 to exchange heat with each other. In the presentembodiment, the subcooling heat exchanger 47 is provided in a portionthat is between the first outdoor expansion valve 44 and the secondoutdoor expansion valve 45 and that is on the side closer than thebranch portion of the subcooling pipe 46 to the second outdoor expansionvalve 45.

The subcooling temperature sensor 67 is a temperature sensor thatdetects the temperature of the refrigerant flowing through a portioncloser than the subcooling heat exchanger 47 to the second outdoorexpansion valve 45 in a portion between the first outdoor expansionvalve 44 and the second outdoor expansion valve 45 in the refrigerantcircuit 10.

(13-2) Cooling Operating Mode

In the air conditioning apparatus 1 g, in the cooling operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the evaporation temperature of therefrigerant in the refrigerant circuit 10 becomes a target evaporationtemperature. In this case, the target evaporation temperature ispreferably determined in accordance with one of the indoor units 30 and35 having the largest difference between the set temperature and theindoor temperature (an indoor unit having the largest load).

The gas refrigerant discharged from the compressor 21 passes through thefour-way switching valve 22 and is condensed in the outdoor heatexchanger 23. The refrigerant which has flowed through the outdoor heatexchanger 23 passes through the first outdoor expansion valve 44. Notethat, in this case, the first outdoor expansion valve 44 is controlledto be in a full-open state.

A portion of the refrigerant which has passed through the first outdoorexpansion valve 44 flows toward the second outdoor expansion valve 45and another portion of the refrigerant is branched and flows to thesubcooling pipe 46. The refrigerant which has been branched and flowedto the subcooling pipe 46 is decompressed at the subcooling expansionvalve 48. The subcooling heat exchanger 47 causes the refrigerantflowing from the first outdoor expansion valve 44 toward the secondoutdoor expansion valve 45, and the refrigerant decompressed at thesubcooling expansion valve 48 and flowing through the subcooling pipe 46to exchange heat with each other. The refrigerant flowing through thesubcooling pipe 46 exchanges heat in the subcooling heat exchanger 47,and then flows to join to a joint portion extending from one of theconnecting ports of the four-way switching valve 22 to the low-pressurereceiver 41. After the heat exchange in the subcooling heat exchanger47, the refrigerant flowing from the first outdoor expansion valve 44toward the second outdoor expansion valve 45 is decompressed at thesecond outdoor expansion valve 45.

As described above, the second outdoor expansion valve 45 is controlledto satisfy a predetermined condition, for example, such that the degreeof subcooling of the refrigerant flowing through the liquid-side outletof the outdoor heat exchanger 23 becomes a target value.

Moreover, the valve opening degree of the subcooling expansion valve 48is controlled such that at least the refrigerant which reaches the firstindoor expansion valve 33 and the second indoor expansion valve 38 is ina gas-liquid two-phase state to prevent occurrence of a situation inwhich all portions extending from the second outdoor expansion valve 45via the liquid-side connection pipe 6 to the first indoor expansionvalve 33 and the second indoor expansion valve 38 are filled with therefrigerant in a liquid state in the refrigerant circuit 10. Forexample, the valve opening degree of the subcooling expansion valve 48is preferably controlled such that the specific enthalpy of therefrigerant which flows from the first outdoor expansion valve 44 towardthe second outdoor expansion valve 45 and which has passed through thesubcooling heat exchanger 47 is larger than the specific enthalpy of aportion in which the low pressure in the refrigeration cycle intersectswith the saturated liquid line in the Mollier diagram. In this case, thecontroller 7 previously stores data in the Mollier diagram correspondingto the refrigerant, and may control the valve opening degree of thesubcooling expansion valve 48 based of the specific enthalpy of therefrigerant which has passed through the subcooling heat exchanger 47acquired from the detected pressure of the discharge pressure sensor 61,the detected temperature of the subcooling temperature sensor 67, andthe data of the Mollier diagram corresponding to the refrigerant. Thevalve opening degree of the subcooling expansion valve 48 is preferablycontrolled to satisfy a predetermined condition, for example, such thatthe temperature of the refrigerant which flows from the first outdoorexpansion valve 44 toward the second outdoor expansion valve 45 andwhich has passed through the subcooling heat exchanger 47 (the detectedtemperature of the subcooling temperature sensor 67) becomes a targetvalue.

The refrigerant decompressed at the second outdoor expansion valve 45passes through the liquid-side shutoff valve 29 and the liquid-sideconnection pipe 6, and is sent to the first indoor unit 30 and thesecond indoor unit 35.

In this case, in the first indoor unit 30, the valve opening degree ofthe first indoor expansion valve 33 is controlled to satisfy apredetermined condition, for example, such that the degree ofsuperheating of the refrigerant flowing through the gas-side outlet ofthe first indoor heat exchanger 31 becomes a target value. Moreover,also for the second indoor expansion valve 38 of the second indoor unit35, similarly to the first indoor expansion valve 33, the valve openingdegree of the second indoor expansion valve 38 is controlled to satisfya predetermined condition, for example, such that the degree ofsuperheating of the refrigerant flowing through the gas-side outlet ofthe second indoor heat exchanger 36 becomes a target value. Each of thevalve opening degrees of the first indoor expansion valve 33 and thesecond indoor expansion valve 38 may be controlled to satisfy apredetermined condition, for example, such that the degree ofsuperheating of the refrigerant obtained by subtracting the saturationtemperature of the refrigerant corresponding to the detected pressure ofthe suction pressure sensor 63 from the detected temperature of thesuction temperature sensor 64. Furthermore, the method of controllingeach of the valve opening degrees of the first indoor expansion valve 33and the second indoor expansion valve 38 is not limited, and, forexample, control may be performed such that the discharge temperature ofthe refrigerant discharged from the compressor 21 becomes apredetermined temperature, or the degree of superheating of therefrigerant discharged from the compressor 21 satisfies a predeterminedcondition.

The refrigerant decompressed at the first indoor expansion valve 33 isevaporated in the first indoor heat exchanger 31, the refrigerantdecompressed at the second indoor expansion valve 38 is evaporated inthe second indoor heat exchanger 36, and the evaporated refrigerants arejoined. Then, the joined refrigerant flows to the gas-side connectionpipe 5. The refrigerant which has flowed through the gas-side connectionpipe 5 passes through the gas-side shutoff valve 28 and the four-wayswitching valve 22, and is joined to the refrigerant which has flowedthrough the subcooling pipe 46. The joined refrigerant passes throughthe low-pressure receiver 41 and is sucked into the compressor 21 again.Note that the low-pressure receiver 41 stores, as an excessiverefrigerant, the liquid refrigerants which have not been completelyevaporated in the first indoor heat exchanger 31, the second indoor heatexchanger 36, and the subcooling heat exchanger 47.

(13-3) Heating Operating Mode

In the air conditioning apparatus 1 g, in the heating operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the condensation temperature ofthe refrigerant in the refrigerant circuit 10 becomes a targetcondensation temperature. In this case, the target condensationtemperature is preferably determined in accordance with one of theindoor units 30 and 35 having the largest difference between the settemperature and the indoor temperature (an indoor unit having thelargest load).

The gas refrigerant discharged from the compressor 21 flows through thefour-way switching valve 22 and the gas-side connection pipe 5 then aportion of the refrigerant flows into the gas-side end of the firstindoor heat exchanger 31 of the first indoor unit 30 and is condensed inthe first indoor heat exchanger 31, and another portion of therefrigerant flows into the gas-side end of the second indoor heatexchanger 36 of the second indoor unit 35 and is condensed in the secondindoor heat exchanger 36.

Note that, the valve opening degree of the first indoor expansion valve33 of the first indoor unit 30 is controlled to satisfy a predeterminedcondition, for example, such that the degree of subcooling of therefrigerant flowing through the liquid side of the first indoor heatexchanger 31 becomes a predetermined target value. Also for the secondindoor expansion valve 38 of the second indoor unit 35, the valveopening degree of the second indoor expansion valve 38 is controlledlikewise to satisfy a predetermined condition, for example, such thatthe degree of subcooling of the refrigerant flowing through the liquidside of the second indoor heat exchanger 36 becomes a predeterminedtarget value.

The refrigerant decompressed at the first indoor expansion valve 33 andthe refrigerant decompressed at the second indoor expansion valve 38 arejoined. The joined refrigerant flows through the liquid-side connectionpipe 6 and flows into the outdoor unit 20.

The refrigerant which has passed through the liquid-side shutoff valve29 of the outdoor unit 20 passes through the second outdoor expansionvalve 45 controlled to be in a full-open state, and exchanges heat withthe refrigerant flowing through the subcooling pipe 46 in the subcoolingheat exchanger 47. A portion of the refrigerant which has passed throughthe second outdoor expansion valve 45 and the subcooling heat exchanger47 is branched to the subcooling pipe 46, and another portion of therefrigerant is sent to the first outdoor expansion valve 44. Therefrigerant which has been branched and flowed to the subcooling pipe 46is decompressed at the subcooling expansion valve 48, and then is joinedto the refrigerant which has flowed from the indoor unit 30 or 35, in ajoint portion between one of the connecting ports of the four-wayswitching valve 22 and the low-pressure receiver 41. The refrigerantwhich has flowed from the subcooling heat exchanger 47 toward the firstoutdoor expansion valve 44 is decompressed at the first outdoorexpansion valve 44, and flows into the outdoor heat exchanger 23.

In this case, the valve opening degree of the first outdoor expansionvalve 44 is controlled to satisfy a predetermined condition, forexample, such that the degree of superheating of the refrigerant flowingthrough the suction side of the compressor 21 becomes a target value.Note that the method of controlling the valve opening degree of thefirst outdoor expansion valve 44 is not limited, and, for example,control may be performed such that the discharge temperature of therefrigerant discharged from the compressor 21 becomes a predeterminedtemperature, or the degree of superheating of the refrigerant dischargedfrom the compressor 21 satisfies a predetermined condition.

Moreover, the valve opening degree of the subcooling expansion valve 48is controlled to satisfy a predetermined condition, for example, suchthat the degree of superheating of the refrigerant flowing through thesuction side of the compressor 21 becomes a target value. Note that themethod of controlling the valve opening degree of the subcoolingexpansion valve 48 is not limited, and, for example, control may beperformed such that the discharge temperature of the refrigerantdischarged from the compressor 21 becomes a predetermined temperature,or the degree of superheating of the refrigerant discharged from thecompressor 21 satisfies a predetermined condition. During heatingoperation, the subcooling expansion valve 48 may be controlled to be ina full-close state to prevent the refrigerant from flowing to thesubcooling pipe 46.

The refrigerant decompressed at the first outdoor expansion valve 44 isevaporated in the outdoor heat exchanger 23, passes through the four-wayswitching valve 22, and is joined to the refrigerant which has flowedthrough the subcooling pipe 46. The joined refrigerant passes throughthe low-pressure receiver 41 and is sucked into the compressor 21 again.Note that the low-pressure receiver 41 stores, as an excessiverefrigerant, the liquid refrigerant which has not been completelyevaporated in the outdoor heat exchanger 23 and the subcooling heatexchanger 47.

(13-4) Characteristics of Eighth Embodiment

Since the air conditioning apparatus 1 g can perform the refrigerationcycle using the refrigerant containing 1,2-difluoroethylene, the airconditioning apparatus 1 g can perform a refrigeration cycle using asmall-GWP refrigerant.

Moreover, since the air conditioning apparatus 1 g is provided with thelow-pressure receiver 41, liquid compression in the compressor 21 can besuppressed. Furthermore, since superheating control is performed on thefirst indoor expansion valve 33 and the second indoor expansion valve 38during cooling operation and subcooling control is performed on thefirst indoor expansion valve 33 and the second indoor expansion valve 38during heating operation, the capacities of the first indoor heatexchanger 31 and the second indoor heat exchanger 36 are likelysufficiently provided.

Furthermore, with the air conditioning apparatus 1 g, during coolingoperation, the space in the pipes from when the refrigerant passesthrough the second outdoor expansion valve 45 to when the refrigerantreaches the first indoor expansion valve 33 and the second indoorexpansion valve 38 via the liquid-side connection pipe 6 is not filledwith the liquid-state refrigerant, and control is performed so that arefrigerant in a gas-liquid two-phase state is in at least a portion ofthe space. As compared with the case where all the space in the pipesextending from the second outdoor expansion valve 45 to the first indoorexpansion valve 33 and the second indoor expansion valve 38 is filledwith the liquid refrigerant, refrigerant concentration can be decreasedin the portion. The refrigeration cycle can be performed while theamount of refrigerant enclosed in the refrigerant circuit 10 isdecreased. Thus, even if the refrigerant leaks from the refrigerantcircuit 10, the leakage amount of refrigerant can be decreased.

(14) Ninth Embodiment

An air conditioning apparatus 1 h serving as a refrigeration cycleapparatus according to a ninth embodiment is described below withreference to FIG. 32 which is a schematic configuration diagram of arefrigerant circuit and FIG. 33 which is a schematic control blockconfiguration diagram. Differences from the air conditioning apparatus 1e according to the sixth embodiment are mainly described below.

(14-1) Schematic Configuration of Air Conditioning Apparatus 1 h

The air conditioning apparatus 1 h differs from the air conditioningapparatus 1 e according to the sixth embodiment in that a suctionrefrigerant heating section 50 is included.

The suction refrigerant heating section 50 is constituted of a portionof the refrigerant pipe that extends from one of the connecting ports ofthe four-way switching valve 22 toward the suction side of thecompressor 21 and that is located in the intermediate-pressure receiver43. In the suction refrigerant heating section 50, the refrigerantflowing through the refrigerant pipe that extends from one of theconnecting ports of the four-way switching valve 22 toward the suctionside of the compressor 21 and the refrigerant in theintermediate-pressure receiver 43 exchange heat with each other withoutmixed with each other.

(14-2) Cooling Operating Mode

In the air conditioning apparatus 1 h, in the cooling operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the evaporation temperature of therefrigerant in the refrigerant circuit 10 becomes a target evaporationtemperature that is determined in accordance with the difference betweenthe set temperature and the indoor temperature (the detected temperatureof the indoor air temperature sensor 72).

The gas refrigerant discharged from the compressor 21 passes through thefour-way switching valve 22 and then is condensed in the outdoor heatexchanger 23. The refrigerant which has flowed through the outdoor heatexchanger 23 is decompressed at the first outdoor expansion valve 44 toan intermediate pressure in the refrigeration cycle.

In this case, the valve opening degree of the first outdoor expansionvalve 44 is controlled to satisfy a predetermined condition, forexample, such that the degree of subcooling of the refrigerant flowingthrough the liquid-side outlet of the outdoor heat exchanger 23 becomesa target value.

The refrigerant decompressed at the first outdoor expansion valve 44flows into the intermediate-pressure receiver 43. Theintermediate-pressure receiver 43 stores, as the liquid refrigerant, anexcessive refrigerant in the refrigerant circuit 10. In this case, therefrigerant which has flowed into the intermediate-pressure receiver 43is cooled through heat exchange with the refrigerant flowing through aportion of the suction refrigerant heating section 50 on the suctionside of the compressor 21. The refrigerant which has cooled in thesuction refrigerant heating section 50 in the intermediate-pressurereceiver 43 is decompressed to a low pressure in the refrigeration cycleat the second outdoor expansion valve 45.

In this case, the valve opening degree of the second outdoor expansionvalve 45 is controlled to satisfy a predetermined condition, forexample, such that the degree of superheating of the refrigerant flowingthrough the gas side of the indoor heat exchanger 31 or the degree ofsuperheating of the refrigerant to be sucked by the compressor 21becomes a target value. Note that the method of controlling the valveopening degree of the second outdoor expansion valve 45 is not limited,and, for example, control may be performed such that the dischargetemperature of the refrigerant discharged from the compressor 21 becomesa predetermined temperature, or the degree of superheating of therefrigerant discharged from the compressor 21 satisfies a predeterminedcondition.

The refrigerant decompressed at the second outdoor expansion valve 45 tothe low pressure in the refrigeration cycle passes through theliquid-side shutoff valve 29 and the liquid-side connection pipe 6,flows into the indoor unit 30, and is evaporated in the indoor heatexchanger 31. The refrigerant which has flowed through the indoor heatexchanger 31 flows through the gas-side connection pipe 5, then passesthrough the gas-side shutoff valve 28 and the four-way switching valve22, and flows inside the refrigerant pipe that passes through the insideof the intermediate-pressure receiver 43. The refrigerant flowing insidethe refrigerant pipe that passes through the inside of theintermediate-pressure receiver 43 is heated through heat exchange withthe refrigerant stored in the intermediate-pressure receiver 43, in thesuction refrigerant heating section 50 in the intermediate-pressurereceiver 43, and is sucked into the compressor 21 again.

(14-3) Heating Operating Mode

In the air conditioning apparatus 1 h, in the heating operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the condensation temperature ofthe refrigerant in the refrigerant circuit 10 becomes a targetcondensation temperature that is determined in accordance with thedifference between the set temperature and the indoor temperature (thedetected temperature of the indoor air temperature sensor 72).

The gas refrigerant discharged from the compressor 21 flows through thefour-way switching valve 22 and the gas-side connection pipe 5, thenflows into the gas-side end of the indoor heat exchanger 31 of theindoor unit 30, and is condensed in the indoor heat exchanger 31. Therefrigerant which has flowed out from the liquid-side end of the indoorheat exchanger 31 flows through the liquid-side connection pipe 6, flowsinto the outdoor unit 20, passes through the liquid-side shutoff valve29, and is decompressed to an intermediate pressure in the refrigerationcycle at the second outdoor expansion valve 45.

In this case, the valve opening degree of the second outdoor expansionvalve 45 is controlled to satisfy a predetermined condition, forexample, such that the degree of subcooling of the refrigerant flowingthrough the liquid-side outlet of the indoor heat exchanger 31 becomes atarget value.

The refrigerant decompressed at the second outdoor expansion valve 45flows into the intermediate-pressure receiver 43. Theintermediate-pressure receiver 43 stores, as the liquid refrigerant, anexcessive refrigerant in the refrigerant circuit 10. In this case, therefrigerant which has flowed into the intermediate-pressure receiver 43is cooled through heat exchange with the refrigerant flowing through aportion of the suction refrigerant heating section 50 on the suctionside of the compressor 21. The refrigerant which has cooled in thesuction refrigerant heating section 50 in the intermediate-pressurereceiver 43 is decompressed to a low pressure in the refrigeration cycleat the first outdoor expansion valve 44.

In this case, the valve opening degree of the first outdoor expansionvalve 44 is controlled to satisfy a predetermined condition, forexample, such that the degree of superheating of the refrigerant to besucked by the compressor 21 becomes a target value. Note that the methodof controlling the valve opening degree of the first outdoor expansionvalve 44 is not limited, and, for example, control may be performed suchthat the discharge temperature of the refrigerant discharged from thecompressor 21 becomes a predetermined temperature, or the degree ofsuperheating of the refrigerant discharged from the compressor 21satisfies a predetermined condition.

The refrigerant decompressed at the first outdoor expansion valve 44 isevaporated in the outdoor heat exchanger 23, passes through the four-wayswitching valve 22, and flows inside the refrigerant pipe that passesthrough the inside of the intermediate-pressure receiver 43. Therefrigerant flowing inside the refrigerant pipe that passes through theinside of the intermediate-pressure receiver 43 is heated through heatexchange with the refrigerant stored in the intermediate-pressurereceiver 43, in the suction refrigerant heating section 50 in theintermediate-pressure receiver 43, and is sucked into the compressor 21again.

(14-4) Characteristics of Ninth Embodiment

Since the air conditioning apparatus 1 h can perform the refrigerationcycle using the refrigerant containing 1,2-difluoroethylene, the airconditioning apparatus 1 h can perform a refrigeration cycle using asmall-GWP refrigerant.

Moreover, since the air conditioning apparatus 1 h is provided with theintermediate-pressure receiver 43, an excessive refrigerant in therefrigerant circuit 10 can be stored. During cooling operation, sincesubcooling control is performed on the first outdoor expansion valve 44,the capacity of the outdoor heat exchanger 23 can be likely sufficientlyprovided. During heating operation, since subcooling control isperformed on the second outdoor expansion valve 45, the capacity of theindoor heat exchanger 31 can be likely sufficiently provided.

Furthermore, since the suction refrigerant heating section 50 isprovided, the refrigerant to be sucked into the compressor 21 is heatedand liquid compression in the compressor 21 is suppressed. Control canbe provided to cause the degree of superheating of the refrigerantflowing through the outlet of the indoor heat exchanger 31 thatfunctions as the evaporator of the refrigerant during cooling operationto be a small value. Also, similarly in heating operation, control canbe provided to cause the degree of superheating of the refrigerantflowing through the outlet of the outdoor heat exchanger 23 thatfunctions as the evaporator of the refrigerant to be a small value.Thus, in either of cooling operation and heating operation, even whenuse of a nonazeotropic mixed refrigerant as the refrigerant causes atemperature glide in the evaporator, the capacity of the heat exchangerthat functions as the evaporator can be sufficiently provided.

(15) Tenth Embodiment

An air conditioning apparatus 1 i serving as a refrigeration cycleapparatus according to a tenth embodiment is described below withreference to FIG. 34 which is a schematic configuration diagram of arefrigerant circuit and FIG. 35 which is a schematic control blockconfiguration diagram. Differences from the air conditioning apparatus 1h according to the ninth embodiment are mainly described below.

(15-1) Schematic Configuration of Air Conditioning Apparatus 1 i

The air conditioning apparatus 1 i differs from the air conditioningapparatus 1 h according to the ninth embodiment in that the firstoutdoor expansion valve 44 and the second outdoor expansion valve 45 arenot provided, the outdoor expansion valve 24 is provided, a plurality ofindoor units (a first indoor unit 30 and a second indoor unit 35) areprovided in parallel, and an indoor expansion valve is provided on theliquid-refrigerant side of an indoor heat exchanger in each indoor unit.

The outdoor expansion valve 24 is provided midway in a refrigerant pipeextending from the liquid-side outlet of the outdoor heat exchanger 23to the intermediate-pressure receiver 43. The outdoor expansion valve 24is preferably an electric expansion valve of which the valve openingdegree is adjustable.

Similarly to the above-described embodiment, the first indoor unit 30includes a first indoor heat exchanger 31 and a first indoor fan 32, anda first indoor expansion valve 33 is provided on the liquid-refrigerantside of the first indoor heat exchanger 31. The first indoor expansionvalve 33 is preferably an electric expansion valve of which the valveopening degree is adjustable. Similarly to the above-describedembodiment, the first indoor unit 30 includes a first indoor-unitcontrol unit 34; and a first indoor liquid-side heat-exchangetemperature sensor 71, a first indoor air temperature sensor 72, and afirst indoor gas-side heat-exchange temperature sensor 73 that areelectrically connected to the first indoor-unit control unit 34.Similarly to the first indoor unit 30, the second indoor unit 35includes a second indoor heat exchanger 36 and a second indoor fan 37,and a second indoor expansion valve 38 is provided on theliquid-refrigerant side of the second indoor heat exchanger 36. Thesecond indoor expansion valve 38 is preferably an electric expansionvalve of which the valve opening degree is adjustable. Similarly to thefirst indoor unit 30, the second indoor unit 35 includes a secondindoor-unit control unit 39; and a second indoor liquid-sideheat-exchange temperature sensor 75, a second indoor air temperaturesensor 76, and a second indoor gas-side heat-exchange temperature sensor77 that are electrically connected to the second indoor-unit controlunit 39.

(15-2) Cooling Operating Mode

In the air conditioning apparatus 1 i, in the cooling operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the evaporation temperature of therefrigerant in the refrigerant circuit 10 becomes a target evaporationtemperature. In this case, the target evaporation temperature ispreferably determined in accordance with one of the indoor units 30 and35 having the largest difference between the set temperature and theindoor temperature (an indoor unit having the largest load).

The gas refrigerant discharged from the compressor 21 passes through thefour-way switching valve 22 and then is condensed in the outdoor heatexchanger 23. The refrigerant which has flowed through the outdoor heatexchanger 23 passes through the outdoor expansion valve 24 controlled tobe in a full-open state.

The refrigerant which has passed through the outdoor expansion valve 24flows into the intermediate-pressure receiver 43. Theintermediate-pressure receiver 43 stores, as the liquid refrigerant, anexcessive refrigerant in the refrigerant circuit 10. In this case, therefrigerant which has flowed into the intermediate-pressure receiver 43is cooled through heat exchange with the refrigerant flowing through aportion of the suction refrigerant heating section 50 on the suctionside of the compressor 21. The refrigerant which has cooled in thesuction refrigerant heating section 50 in the intermediate-pressurereceiver 43 passes through the liquid-side shutoff valve 29 and theliquid-side connection pipe 6, and flows into the first indoor unit 30and the second indoor unit 35.

The refrigerant which has flowed into the first indoor unit 30 isdecompressed at the first indoor expansion valve 33 to a low pressure inthe refrigeration cycle. The refrigerant which has flowed into thesecond indoor unit 35 is decompressed at the second indoor expansionvalve 38 to a low pressure in the refrigeration cycle.

In this case, the valve opening degree of the first indoor expansionvalve 33 is controlled to satisfy a predetermined condition, forexample, such that the degree of superheating of the refrigerant flowingthrough the gas side of the first indoor heat exchanger 31 or the degreeof superheating of the refrigerant to be sucked by the compressor 21becomes a target value. Moreover, the valve opening degree of the secondindoor expansion valve 38 is controlled to satisfy a predeterminedcondition, for example, such that the degree of superheating of therefrigerant flowing through the gas side of the second indoor heatexchanger 36 or the degree of superheating of the refrigerant to besucked by the compressor 21 becomes a target value.

The refrigerant decompressed at the first indoor expansion valve 33 isevaporated in the first indoor heat exchanger 31, the refrigerantdecompressed at the second indoor expansion valve 38 is evaporated inthe second indoor heat exchanger 36, and the evaporated refrigerants arejoined. Then, the joined refrigerant flows through the gas-sideconnection pipe 5, the gas-side shutoff valve 28, and the four-wayswitching valve 22, and flows inside the refrigerant pipe that passesthrough the inside of the intermediate-pressure receiver 43. Therefrigerant flowing inside the refrigerant pipe that passes through theinside of the intermediate-pressure receiver 43 is heated through heatexchange with the refrigerant stored in the intermediate-pressurereceiver 43, in the suction refrigerant heating section 50 in theintermediate-pressure receiver 43, and is sucked into the compressor 21again.

(15-3) Heating Operating Mode

In the air conditioning apparatus 1 i, in the heating operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the condensation temperature ofthe refrigerant in the refrigerant circuit 10 becomes a targetcondensation temperature. In this case, the target condensationtemperature is preferably determined in accordance with one of theindoor units 30 and 35 having the largest difference between the settemperature and the indoor temperature (an indoor unit having thelargest load).

The gas refrigerant discharged from the compressor 21 flows through thefour-way switching valve 22 and the gas-side connection pipe 5, and thenflows into each of the first indoor unit 30 and the second indoor unit35.

The refrigerant which has flowed into the first indoor unit 30 iscondensed in the first indoor heat exchanger 31. The refrigerant whichhas flowed into the second indoor unit 35 is condensed in the secondindoor heat exchanger 36.

The refrigerant which has flowed out from the liquid-side end of thefirst indoor heat exchanger 31 is decompressed at the first indoorexpansion valve 33 to an intermediate pressure in the refrigerationcycle. The refrigerant which has flowed out from the liquid-side end ofthe second indoor heat exchanger 36 is decompressed at the second indoorexpansion valve 38 to an intermediate pressure in the refrigerationcycle.

In this case, the valve opening degree of the first indoor expansionvalve 33 is controlled to satisfy a predetermined condition, forexample, such that the degree of subcooling of the refrigerant flowingthrough the liquid-side outlet of the first indoor heat exchanger 31becomes a target value. Also, the valve opening degree of the secondindoor expansion valve 38 is controlled to satisfy a predeterminedcondition, for example, such that the degree of subcooling of therefrigerant flowing through the liquid-side outlet of the second indoorheat exchanger 36 becomes a target value.

The refrigerant which has passed through the first indoor expansionvalve 33 and the refrigerant which has passed through the second indoorexpansion valve 38 are joined. Then, the joined refrigerant passesthrough the liquid-side connection pipe 6 and flows into the outdoorunit 20.

The refrigerant which has flowed into the outdoor unit 20 passes throughthe liquid-side shutoff valve 29, and flows into theintermediate-pressure receiver 43. The intermediate-pressure receiver 43stores, as the liquid refrigerant, an excessive refrigerant in therefrigerant circuit 10. In this case, the refrigerant which has flowedinto the intermediate-pressure receiver 43 is cooled through heatexchange with the refrigerant flowing through a portion of the suctionrefrigerant heating section 50 on the suction side of the compressor 21.The refrigerant which has cooled in the suction refrigerant heatingsection 50 in the intermediate-pressure receiver 43 is decompressed to alow pressure in the refrigeration cycle at the outdoor expansion valve24.

In this case, the valve opening degree of the outdoor expansion valve 24is controlled to satisfy a predetermined condition, for example, suchthat the degree of superheating of the refrigerant to be sucked by thecompressor 21 becomes a target value. Note that the method ofcontrolling the valve opening degree of the outdoor expansion valve 24is not limited, and, for example, control may be performed such that thedischarge temperature of the refrigerant discharged from the compressor21 becomes a predetermined temperature, or the degree of superheating ofthe refrigerant discharged from the compressor 21 satisfies apredetermined condition.

The refrigerant decompressed at the outdoor expansion valve 24 isevaporated in the outdoor heat exchanger 23, passes through the four-wayswitching valve 22, and flows inside the refrigerant pipe that passesthrough the inside of the intermediate-pressure receiver 43. Therefrigerant flowing inside the refrigerant pipe that passes through theinside of the intermediate-pressure receiver 43 is heated through heatexchange with the refrigerant stored in the intermediate-pressurereceiver 43, in the suction refrigerant heating section 50 in theintermediate-pressure receiver 43, and is sucked into the compressor 21again.

(15-4) Characteristics of Tenth Embodiment

Since the air conditioning apparatus 1 i can perform the refrigerationcycle using the refrigerant containing 1,2-difluoroethylene, the airconditioning apparatus 1 i can perform a refrigeration cycle using asmall-GWP refrigerant.

Moreover, since the air conditioning apparatus 1 i is provided with theintermediate-pressure receiver 43, an excessive refrigerant in therefrigerant circuit 10 can be stored. During heating operation, sincesubcooling control is performed on the second outdoor expansion valve45, the capacity of the indoor heat exchanger 31 can be likelysufficiently provided.

Furthermore, since the suction refrigerant heating section 50 isprovided, the refrigerant to be sucked into the compressor 21 is heatedand liquid compression in the compressor 21 is suppressed. Control canbe provided to cause the degree of superheating of the refrigerantflowing through the outlet of the indoor heat exchanger 31 thatfunctions as the evaporator of the refrigerant during cooling operationto be a small value. Also, similarly in heating operation, control canbe provided to cause the degree of superheating of the refrigerantflowing through the outlet of the outdoor heat exchanger 23 thatfunctions as the evaporator of the refrigerant to be a small value.Thus, in either of cooling operation and heating operation, even whenuse of a nonazeotropic mixed refrigerant as the refrigerant causes atemperature glide in the evaporator, the capacity of the heat exchangerthat functions as the evaporator can be sufficiently provided.

(16) Eleventh Embodiment

An air conditioning apparatus 1 j serving as a refrigeration cycleapparatus according to an eleventh embodiment is described below withreference to FIG. 36 which is a schematic configuration diagram of arefrigerant circuit and FIG. 37 which is a schematic control blockconfiguration diagram. Differences from the air conditioning apparatus 1h according to the ninth embodiment are mainly described below.

(16-1) Schematic Configuration of Air Conditioning Apparatus 1 j

The air conditioning apparatus 1 j differs from the air conditioningapparatus 1 h according to the ninth embodiment in that the suctionrefrigerant heating section 50 is not provided and an internal heatexchanger 51 is provided.

The internal heat exchanger 51 is a heat exchanger that exchanges heatbetween the refrigerant flowing between the first outdoor expansionvalve 44 and the second outdoor expansion valve 45 and the refrigerantflowing through the refrigerant pipe extending from one of theconnecting ports of the four-way switching valve 22 toward the suctionside of the compressor 21.

(16-2) Cooling Operating Mode

In the air conditioning apparatus 1 j, in the cooling operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the evaporation temperature of therefrigerant in the refrigerant circuit 10 becomes a target evaporationtemperature that is determined in accordance with the difference betweenthe set temperature and the indoor temperature (the detected temperatureof the indoor air temperature sensor 72).

The gas refrigerant discharged from the compressor 21 passes through thefour-way switching valve 22 and then is condensed in the outdoor heatexchanger 23. The refrigerant which has flowed through the outdoor heatexchanger 23 passes through the first outdoor expansion valve 44controlled to be in a full-open state. The refrigerant which has passedthrough the first outdoor expansion valve 44 is cooled in the internalheat exchanger 51 and decompressed to a low pressure in therefrigeration cycle at the second outdoor expansion valve 45.

In this case, the valve opening degree of the second outdoor expansionvalve 45 is controlled to satisfy a predetermined condition, forexample, such that the degree of superheating of the refrigerant flowingthrough the gas side of the indoor heat exchanger 31 or the degree ofsuperheating of the refrigerant to be sucked by the compressor 21becomes a target value. Note that the method of controlling the valveopening degree of the second outdoor expansion valve 45 is not limited,and, for example, control may be performed such that the dischargetemperature of the refrigerant discharged from the compressor 21 becomesa predetermined temperature, or the degree of superheating of therefrigerant discharged from the compressor 21 satisfies a predeterminedcondition.

The refrigerant decompressed at the second outdoor expansion valve 45 tothe low pressure in the refrigeration cycle passes through theliquid-side shutoff valve 29 and the liquid-side connection pipe 6,flows into the indoor unit 30, and is evaporated in the indoor heatexchanger 31. The refrigerant which has flowed through the indoor heatexchanger 31 flows through the gas-side connection pipe 5, then passesthrough the gas-side shutoff valve 28 and the four-way switching valve22, is heated in the internal heat exchanger 51, and is sucked into thecompressor 21 again.

(16-3) Heating Operating Mode

In the air conditioning apparatus 1 j, in the heating operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the condensation temperature ofthe refrigerant in the refrigerant circuit 10 becomes a targetcondensation temperature that is determined in accordance with thedifference between the set temperature and the indoor temperature (thedetected temperature of the indoor air temperature sensor 72).

The gas refrigerant discharged from the compressor 21 flows through thefour-way switching valve 22 and the gas-side connection pipe 5, thenflows into the gas-side end of the indoor heat exchanger 31 of theindoor unit 30, and is condensed in the indoor heat exchanger 31. Therefrigerant which has flowed out from the liquid-side end of the indoorheat exchanger 31 flows through the liquid-side connection pipe 6, flowsinto the outdoor unit 20, passes through the liquid-side shutoff valve29, and passes through the second outdoor expansion valve 45 controlledto be in a full-open state. The refrigerant which has passed through thesecond outdoor expansion valve 45 is cooled in the internal heatexchanger 51 and decompressed to an intermediate pressure in therefrigeration cycle at the first outdoor expansion valve 44.

In this case, the valve opening degree of the first outdoor expansionvalve 44 is controlled to satisfy a predetermined condition, forexample, such that the degree of superheating of the refrigerant to besucked by the compressor 21 becomes a target value. Note that the methodof controlling the valve opening degree of the first outdoor expansionvalve 44 is not limited, and, for example, control may be performed suchthat the discharge temperature of the refrigerant discharged from thecompressor 21 becomes a predetermined temperature, or the degree ofsuperheating of the refrigerant discharged from the compressor 21satisfies a predetermined condition.

The refrigerant decompressed at the first outdoor expansion valve 44 isevaporated in the outdoor heat exchanger 23, passes through the four-wayswitching valve 22, is heated in the internal heat exchanger 51, and issucked into the compressor 21 again.

(16-4) Characteristics of Eleventh Embodiment

Since the air conditioning apparatus 1 j can perform the refrigerationcycle using the refrigerant containing 1,2-difluoroethylene, the airconditioning apparatus 1 j can perform a refrigeration cycle using asmall-GWP refrigerant.

Furthermore, since the air conditioning apparatus 1 j is provided withthe internal heat exchanger 51, the refrigerant to be sucked into thecompressor 21 is heated and liquid compression in the compressor 21 issuppressed. Control can be provided to cause the degree of superheatingof the refrigerant flowing through the outlet of the indoor heatexchanger 31 that functions as the evaporator of the refrigerant duringcooling operation to be a small value. Also, similarly in heatingoperation, control can be provided to cause the degree of superheatingof the refrigerant flowing through the outlet of the outdoor heatexchanger 23 that functions as the evaporator of the refrigerant to be asmall value. Thus, in either of cooling operation and heating operation,even when use of a nonazeotropic mixed refrigerant as the refrigerantcauses a temperature glide in the evaporator, the capacity of the heatexchanger that functions as the evaporator can be sufficiently provided.

(17) Twelfth Embodiment

An air conditioning apparatus 1 k serving as a refrigeration cycleapparatus according to a twelfth embodiment is described below withreference to FIG. 38 which is a schematic configuration diagram of arefrigerant circuit and FIG. 39 which is a schematic control blockconfiguration diagram. Differences from the air conditioning apparatus 1j according to the tenth embodiment are mainly described below.

(17-1) Schematic Configuration of Air Conditioning Apparatus 1 k

The air conditioning apparatus 1 k differs from the air conditioningapparatus 1 j according to the tenth embodiment in that the firstoutdoor expansion valve 44 and the second outdoor expansion valve 45 arenot provided, but an outdoor expansion valve 24 is provided; a pluralityof indoor units (a first indoor unit 30 and a second indoor unit 35) areprovided in parallel; and an indoor expansion valve is provided on theliquid-refrigerant side of an indoor heat exchanger in each indoor unit.

The outdoor expansion valve 24 is provided midway in the refrigerantpipe extending from the internal heat exchanger 51 to the liquid-sideshutoff valve 29. The outdoor expansion valve 24 is preferably anelectric expansion valve of which the valve opening degree isadjustable.

Similarly to the above-described embodiment, the first indoor unit 30includes a first indoor heat exchanger 31 and a first indoor fan 32, anda first indoor expansion valve 33 is provided on the liquid-refrigerantside of the first indoor heat exchanger 31. The first indoor expansionvalve 33 is preferably an electric expansion valve of which the valveopening degree is adjustable. Similarly to the above-describedembodiment, the first indoor unit 30 includes a first indoor-unitcontrol unit 34, and a first indoor liquid-side heat-exchangetemperature sensor 71, a first indoor air temperature sensor 72, and afirst indoor gas-side heat-exchange temperature sensor 73 that areelectrically connected to the first indoor-unit control unit 34.Similarly to the first indoor unit 30, the second indoor unit 35includes a second indoor heat exchanger 36 and a second indoor fan 37,and a second indoor expansion valve 38 is provided on theliquid-refrigerant side of the second indoor heat exchanger 36. Thesecond indoor expansion valve 38 is preferably an electric expansionvalve of which the valve opening degree is adjustable. Similarly to thefirst indoor unit 30, the second indoor unit 35 includes a secondindoor-unit control unit 39, and a second indoor liquid-sideheat-exchange temperature sensor 75, a second indoor air temperaturesensor 76, and a second indoor gas-side heat-exchange temperature sensor77 that are electrically connected to the second indoor-unit controlunit 39.

(17-2) Cooling Operating Mode

In the air conditioning apparatus 1 k, in the cooling operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the evaporation temperature of therefrigerant in the refrigerant circuit 10 becomes a target evaporationtemperature. In this case, the target evaporation temperature ispreferably determined in accordance with one of the indoor units 30 and35 having the largest difference between the set temperature and theindoor temperature (an indoor unit having the largest load).

The gas refrigerant discharged from the compressor 21 passes through thefour-way switching valve 22 and then is condensed in the outdoor heatexchanger 23. The refrigerant which has flowed through the outdoor heatexchanger 23 is cooled in the internal heat exchanger 51, passes throughthe outdoor expansion valve 24 controlled to be in a full-open state,passes through the liquid-side shutoff valve 29, and the liquid-sideconnection pipe 6, and flows into each of the first indoor unit 30 andthe second indoor unit 35.

The refrigerant which has flowed into the first indoor unit 30 isdecompressed at the first indoor expansion valve 33 to a low pressure inthe refrigeration cycle. The refrigerant which has flowed into thesecond indoor unit 35 is decompressed at the second indoor expansionvalve 38 to a low pressure in the refrigeration cycle.

In this case, the valve opening degree of the first indoor expansionvalve 33 is controlled to satisfy a predetermined condition, forexample, such that the degree of superheating of the refrigerant flowingthrough the gas side of the first indoor heat exchanger 31 or the degreeof superheating of the refrigerant to be sucked by the compressor 21becomes a target value. Moreover, likewise, the valve opening degree ofthe second indoor expansion valve 38 is also controlled to satisfy apredetermined condition, for example, such that the degree ofsuperheating of the refrigerant flowing through the gas side of thesecond indoor heat exchanger 36 or the degree of superheating of therefrigerant to be sucked by the compressor 21 becomes a target value.

The refrigerant decompressed at the first indoor expansion valve 33 isevaporated in the first indoor heat exchanger 31, the refrigerantdecompressed at the second indoor expansion valve 38 is evaporated inthe second indoor heat exchanger 36, and the evaporated refrigerants arejoined. Then, the joined refrigerant flows through the gas-sideconnection pipe 5, passes through the gas-side shutoff valve 28 and thefour-way switching valve 22, is heated in the internal heat exchanger51, and is sucked by the compressor 21 again.

(17-3) Heating Operating Mode

In the air conditioning apparatus 1 k, in the heating operating mode,capacity control is performed on the operating frequency of thecompressor 21, for example, such that the condensation temperature ofthe refrigerant in the refrigerant circuit 10 becomes a targetcondensation temperature. In this case, the target condensationtemperature is preferably determined in accordance with one of theindoor units 30 and 35 having the largest difference between the settemperature and the indoor temperature (an indoor unit having thelargest load).

The gas refrigerant discharged from the compressor 21 flows through thefour-way switching valve 22 and the gas-side connection pipe 5, and thenflows into each of the first indoor unit 30 and the second indoor unit35.

The refrigerant which has flowed into the first indoor unit 30 iscondensed in the first indoor heat exchanger 31. The refrigerant whichhas flowed into the second indoor unit 35 is condensed in the secondindoor heat exchanger 36.

The refrigerant which has flowed out from the liquid-side end of thefirst indoor heat exchanger 31 is decompressed at the first indoorexpansion valve 33 to an intermediate pressure in the refrigerationcycle. The refrigerant which has flowed out from the liquid-side end ofthe second indoor heat exchanger 36 is also likewise decompressed at thesecond indoor expansion valve 38 to an intermediate pressure in therefrigeration cycle.

In this case, the valve opening degree of the first indoor expansionvalve 33 is controlled to satisfy a predetermined condition, forexample, such that the degree of subcooling of the refrigerant flowingthrough the liquid-side outlet of the first indoor heat exchanger 31becomes a target value. Also, the valve opening degree of the secondindoor expansion valve 38 is controlled to satisfy a predeterminedcondition, for example, such that the degree of subcooling of therefrigerant flowing through the liquid-side outlet of the second indoorheat exchanger 36 becomes a target value.

The refrigerant which has passed through the first indoor expansionvalve 33 and the refrigerant which has passed through the second indoorexpansion valve 38 are joined. Then, the joined refrigerant passesthrough the liquid-side connection pipe 6 and flows into the outdoorunit 20.

The refrigerant which has flowed into the outdoor unit 20 passes throughthe liquid-side shutoff valve 29 and is decompressed at the outdoorexpansion valve 24 to a low pressure in the refrigeration cycle.

In this case, the valve opening degree of the outdoor expansion valve 24is controlled to satisfy a predetermined condition, for example, suchthat the degree of superheating of the refrigerant to be sucked by thecompressor 21 becomes a target value. Note that the method ofcontrolling the valve opening degree of the outdoor expansion valve 24is not limited, and, for example, control may be performed such that thedischarge temperature of the refrigerant discharged from the compressor21 becomes a predetermined temperature, or the degree of superheating ofthe refrigerant discharged from the compressor 21 satisfies apredetermined condition.

The refrigerant decompressed at the outdoor expansion valve 24 isevaporated in the outdoor heat exchanger 23, passes through the four-wayswitching valve 22, is heated in the internal heat exchanger 51, and issucked into the compressor 21 again.

(17-4) Characteristics of Twelfth Embodiment

Since the air conditioning apparatus 1 k can perform the refrigerationcycle using the refrigerant containing 1,2-difluoroethylene, the airconditioning apparatus 1 k can perform a refrigeration cycle using asmall-GWP refrigerant.

In the air conditioning apparatus 1 k, during heating operation, sincesubcooling control is performed on the first indoor expansion valve 33and the second indoor expansion valve 38, the capacities of the firstindoor heat exchanger 31 and the second indoor heat exchanger 36 can belikely sufficiently provided.

Furthermore, since the air conditioning apparatus 1 k is provided withthe internal heat exchanger 51, the refrigerant to be sucked into thecompressor 21 is heated and liquid compression in the compressor 21 issuppressed. Control can be provided to cause the degrees of superheatingof the refrigerant flowing through the outlets of the first indoor heatexchanger 31 and the second indoor heat exchanger 36 that function asthe evaporators of the refrigerant during cooling operation to be smallvalues. Also, similarly in heating operation, control can be provided tocause the degree of superheating of the refrigerant flowing through theoutlet of the outdoor heat exchanger 23 that functions as the evaporatorof the refrigerant to be a small value. Thus, in either of coolingoperation and heating operation, even when use of a nonazeotropic mixedrefrigerant as the refrigerant causes a temperature glide in theevaporator, the capacity of the heat exchanger that functions as theevaporator can be sufficiently provided.

The embodiments of the present disclosure have been described above, andit is understood that the embodiments and details can be modified invarious ways without departing from the idea and scope of the presentdisclosure described in the claims.

REFERENCE SIGNS LIST

-   -   1, 1 a to 1 m air conditioning apparatus (refrigeration cycle        apparatus)    -   7 controller (control unit)    -   10 refrigerant circuit    -   20 outdoor unit    -   21 compressor    -   23 outdoor heat exchanger (condenser, evaporator)    -   24 outdoor expansion valve (decompressing section)    -   25 outdoor fan    -   26 indoor bridge circuit    -   27 outdoor-unit control unit (control unit)    -   30 indoor unit, first indoor unit    -   31 indoor heat exchanger, first indoor heat exchanger        (evaporator, condenser)    -   32 indoor fan, first indoor fan    -   33 indoor expansion valve, first indoor expansion valve        (decompressing section)    -   34 indoor-unit control unit, first indoor-unit control unit        (control unit)    -   35 second indoor unit    -   36 second indoor heat exchanger (evaporator, condenser)    -   37 second indoor fan    -   38 second indoor expansion valve (decompressing section)    -   39 second indoor-unit control unit (control unit)    -   40 bypass pipe    -   41 low-pressure receiver    -   42 high-pressure receiver    -   43 intermediate-pressure receiver    -   44 first outdoor expansion valve (decompressing section, first        decompressing section)    -   45 second outdoor expansion valve (decompressing section, second        decompressing section)    -   46 subcooling pipe    -   47 subcooling heat exchanger    -   48 subcooling expansion valve    -   49 bypass expansion valve    -   50 suction refrigerant heating section (refrigerant heat        exchanging section)    -   51 internal heat exchanger (refrigerant heat exchanging section)    -   53 outdoor bridge circuit    -   54 indoor bridge circuit, first indoor bridge circuit    -   55 second indoor bridge circuit    -   61 discharge pressure sensor    -   62 discharge temperature sensor    -   63 suction pressure sensor    -   64 suction temperature sensor    -   65 outdoor heat-exchange temperature sensor    -   66 outdoor air temperature sensor    -   67 subcooling temperature sensor    -   71 indoor liquid-side heat-exchange temperature sensor, first        indoor liquid-side heat-exchange temperature sensor    -   72 indoor air temperature sensor, first indoor air temperature        sensor    -   73 indoor gas-side heat-exchange temperature sensor, first        indoor gas-side heat-exchange temperature sensor    -   75 second indoor liquid-side heat-exchange temperature sensor    -   76 second indoor air temperature sensor    -   77 second indoor gas-side heat-exchange temperature sensor    -   81 indoor inflow-side heat-exchange temperature sensor, first        indoor inflow-side heat-exchange temperature sensor    -   83 indoor outflow-side heat-exchange temperature sensor, first        indoor outflow-side heat-exchange temperature sensor    -   85 second indoor inflow-side heat-exchange temperature sensor    -   87 second indoor outflow-side heat-exchange temperature sensor

CITATION LIST Patent Literature

PTL 1: International Publication No. 2015/141678

The invention claimed is:
 1. A refrigeration cycle apparatus comprising:a refrigerant circuit including a compressor, a condenser, adecompressing section, and an evaporator; and a refrigerant enclosed inthe refrigerant circuit, wherein the refrigerant comprisestrans-1,2-difluoroethylene (HFO-1132(E)), difluoromethane(R32), and2,3,3,3-tetrafluoro-1-propene (R1234yf), wherein when the mass % ofHFO-1132(E), R32, and R1234yf based on their sum in the refrigerant isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), R32, andR1234yf is 100 mass % are within the range of a figure surrounded byline segments IJ, JN, NE, and EI that connect the following 4 points:point I (72.0, 0.0, 28.0), point J (48.5, 18.3, 33.2), point N (27.7,18.2, 54.1), and point E (58.3, 0.0, 41.7), or on these line segments(excluding the points on the line segment EI, the line segment IJ isrepresented by coordinates (0.0236y²-1.7616y+72.0, y,−0.0236y²+0.7616y+28.0); the line segment NE is represented bycoordinates (0.012y²-1.9003y+58.3, y, −0.012y²+0.9003y+41.7); and theline segments JN and EI are straight lines.
 2. The refrigeration cycleapparatus according to claim 1, wherein the refrigerant circuit furtherincludes a low-pressure receiver provided midway in a refrigerant flowpath extending from the evaporator toward a suction side of thecompressor.
 3. The refrigeration cycle apparatus according to claim 1,wherein the refrigerant circuit further includes a high-pressurereceiver provided midway in a refrigerant flow path extending from thecondenser toward the evaporator.
 4. The refrigeration cycle apparatusaccording to claim 1, wherein the decompressing section comprises afirst decompressing section and a second decompressing section, therefrigerant circuit further includes the first decompressing section,the second decompressing section, and an intermediate-pressure receiverprovided midway in a refrigerant flow path extending from the condensertoward the evaporator, and the intermediate-pressure receiver isprovided between the first decompressing section and the seconddecompressing section in the refrigerant flow path extending from thecondenser toward the evaporator.
 5. The refrigeration cycle apparatusaccording to claim 1, wherein the decompressing section comprises afirst decompressing section and a second decompressing section, therefrigerant circuit further includes the first decompressing section andthe second decompressing section provided midway in a refrigerant flowpath extending from the condenser toward the evaporator, and therefrigeration cycle apparatus further comprises a control unit thatadjusts both a degree of decompression of a refrigerant passing throughthe first decompressing section and a degree of decompression of arefrigerant passing through the second decompressing section.
 6. Therefrigeration cycle apparatus according to claim 1, wherein therefrigerant circuit further includes a refrigerant heat exchangingsection that causes a refrigerant flowing from the condenser toward theevaporator and a refrigerant flowing from the evaporator toward thecompressor to exchange heat with each other.
 7. A refrigeration cycleapparatus comprising: a refrigerant circuit including a compressor, acondenser, a decompressing section, and an evaporator; and a refrigerantenclosed in the refrigerant circuit, wherein the refrigerant comprisestrans-1,2-difluoroethylene (HFO-1132(E)), difluoromethane (R32), and2,3,3,3-tetrafluoro-1-propene (R1234yf), wherein when the mass % ofHFO-1132(E), R32, and R1234yf based on their sum in the refrigerant isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), R32, andR1234yf is 100 mass % are within the range of a figure surrounded byline segments MM′, MN, NV, VG, and GM that connect the following 5points: point M (52.6, 0.0, 47.4), point M′(39.2, 5.0, 55.8), point N(27.7, 18.2, 54.1), point V (11.0, 18.1, 70.9), and point G (39.6, 0.0,60.4), or on these line segments (excluding the points on the linesegment GM); the line segment MM′ is represented by coordinates(0.132y²-3.34y+52.6, y, −0.132y²+2.34y+47.4); the line segment M′N isrepresented by coordinates (0.0596y²-2.2541y+48.98, y,−0.0596y²+1.2541y+51.02); the line segment VG is represented bycoordinates (0.0123y²-1.8033y+39.6, y, −0.0123y²+0.8033y+60.4); and theline segments NV and GM are straight lines.
 8. The refrigeration cycleapparatus according to claim 7, wherein the refrigerant circuit furtherincludes a low-pressure receiver provided midway in a refrigerant flowpath extending from the evaporator toward a suction side of thecompressor.
 9. The refrigeration cycle apparatus according to claim 7,wherein the refrigerant circuit further includes a high-pressurereceiver provided midway in a refrigerant flow path extending from thecondenser toward the evaporator.
 10. The refrigeration cycle apparatusaccording to claim 7, wherein the decompressing section comprises afirst decompressing section and a second decompressing section, therefrigerant circuit further includes the first decompressing section,the second decompressing section, and an intermediate-pressure receiverprovided midway in a refrigerant flow path extending from the condensertoward the evaporator, and the intermediate-pressure receiver isprovided between the first decompressing section and the seconddecompressing section in the refrigerant flow path extending from thecondenser toward the evaporator.
 11. The refrigeration cycle apparatusaccording to claim 7, wherein the decompressing section comprises afirst decompressing section and a second decompressing section, therefrigerant circuit further includes the first decompressing section andthe second decompressing section provided midway in a refrigerant flowpath extending from the condenser toward the evaporator, and therefrigeration cycle apparatus further comprises a control unit thatadjusts both a degree of decompression of a refrigerant passing throughthe first decompressing section and a degree of decompression of arefrigerant passing through the second decompressing section.
 12. Therefrigeration cycle apparatus according to claim 7, wherein therefrigerant circuit further includes a refrigerant heat exchangingsection that causes a refrigerant flowing from the condenser toward theevaporator and a refrigerant flowing from the evaporator toward thecompressor to exchange heat with each other.
 13. A refrigeration cycleapparatus comprising: a refrigerant circuit including a compressor, acondenser, a decompressing section, and an evaporator; and a refrigerantenclosed in the refrigerant circuit, wherein the refrigerant comprisestrans-1,2-difluoroethylene (HFO-1132(E)), difluoromethane (R32), and2,3,3,3-tetrafluoro-1-propene (R1234yf), wherein when the mass % ofHFO-1132(E), R32, and R1234yf based on their sum in the refrigerant isrespectively represented by x, y and z, coordinates (x,y,z) in a ternarycomposition diagram in which the sum of HFO-1132(E), R32, and R1234yf is100 mass % are within the range of a figure surrounded by line segmentsON, NU, and UO that connect the following 3 points: point O (22.6, 36.8,40.6), point N (27.7, 18.2, 54.1), and point U (3.9, 36.7, 59.4), or onthese line segments; the line segment ON is represented by coordinates(0.0072y²-0.6701y+37.512, y, −0.0072y²-0.3299y+62.488); the line segmentNU is represented by coordinates (0.0083y²-1.7403y+56.635, y,−0.0083y²+0.7403y+43.365); and the line segment UO is a straight line.14. The refrigeration cycle apparatus according to claim 13, wherein therefrigerant circuit further includes a low-pressure receiver providedmidway in a refrigerant flow path extending from the evaporator toward asuction side of the compressor.
 15. The refrigeration cycle apparatusaccording to claim 13, wherein the refrigerant circuit further includesa high-pressure receiver provided midway in a refrigerant flow pathextending from the condenser toward the evaporator.
 16. Therefrigeration cycle apparatus according to claim 13, wherein thedecompressing section comprises a first decompressing section and asecond decompressing section, the refrigerant circuit further includesthe first decompressing section, the second decompressing section, andan intermediate-pressure receiver provided midway in a refrigerant flowpath extending from the condenser toward the evaporator, and theintermediate-pressure receiver is provided between the firstdecompressing section and the second decompressing section in therefrigerant flow path extending from the condenser toward theevaporator.
 17. The refrigeration cycle apparatus according to claim 13,wherein the decompressing section comprises a first decompressingsection and a second decompressing section, the refrigerant circuitfurther includes the first decompressing section and the seconddecompressing section provided midway in a refrigerant flow pathextending from the condenser toward the evaporator, and therefrigeration cycle apparatus further comprises a control unit thatadjusts both a degree of decompression of a refrigerant passing throughthe first decompressing section and a degree of decompression of arefrigerant passing through the second decompressing section.
 18. Therefrigeration cycle apparatus according to claim 13, wherein therefrigerant circuit further includes a refrigerant heat exchangingsection that causes a refrigerant flowing from the condenser toward theevaporator and a refrigerant flowing from the evaporator toward thecompressor to exchange heat with each other.
 19. A refrigeration cycleapparatus comprising: a refrigerant circuit including a compressor, acondenser, a decompressing section, and an evaporator; and a refrigerantenclosed in the refrigerant circuit, wherein the refrigerant comprisestrans-1,2-difluoroethylene (HFO-1132(E)), difluoromethane (R32), and2,3,3,3-tetrafluoro-1-propene (R1234yf), wherein when the mass % ofHFO-1132(E), R32, and R1234yf based on their sum in the refrigerant isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), R32, andR1234yf is 100 mass % are within the range of a figure surrounded byline segments QR, RT, TL, LK, and KQ that connect the following 5points: point Q (44.6, 23.0, 32.4), point R (25.5, 36.8, 37.7), point T(8.6, 51.6, 39.8), point L (28.9, 51.7, 19.4), and point K (35.6, 36.8,27.6), or on these line segments; the line segment QR is represented bycoordinates (0.0099y²-1.975y+84.765, y, −0.0099y²+0.975y+15.235); theline segment RT is represented by coordinates (0.0082y²-1.8683y+83.126,y, −0.0082y²+0.8683y+16.874); the line segment LK is represented bycoordinates (0.0049y²-0.8842y+61.488, y, −0.0049y²-0.1158y+38.512); theline segment KQ is represented by coordinates (0.0095y²-1.2222y+67.676,y, −0.0095y²+0.2222y+32.324); and the line segment TL is a straightline.
 20. The refrigeration cycle apparatus according to claim 19,wherein the refrigerant circuit further includes a low-pressure receiverprovided midway in a refrigerant flow path extending from the evaporatortoward a suction side of the compressor.
 21. The refrigeration cycleapparatus according to claim 19, wherein the refrigerant circuit furtherincludes a high-pressure receiver provided midway in a refrigerant flowpath extending from the condenser toward the evaporator.
 22. Therefrigeration cycle apparatus according to claim 19, wherein thedecompressing section comprises a first decompressing section and asecond decompressing section, the refrigerant circuit further includesthe first decompressing section, the second decompressing section, andan intermediate-pressure receiver provided midway in a refrigerant flowpath extending from the condenser toward the evaporator, and theintermediate-pressure receiver is provided between the firstdecompressing section and the second decompressing section in therefrigerant flow path extending from the condenser toward theevaporator.
 23. The refrigeration cycle apparatus according to claim 19,wherein the decompressing section comprises a first decompressingsection and a second decompressing section, the refrigerant circuitfurther includes the first decompressing section and the seconddecompressing section provided midway in a refrigerant flow pathextending from the condenser toward the evaporator, and therefrigeration cycle apparatus further comprises a control unit thatadjusts both a degree of decompression of a refrigerant passing throughthe first decompressing section and a degree of decompression of arefrigerant passing through the second decompressing section.
 24. Therefrigeration cycle apparatus according to claim 19, wherein therefrigerant circuit further includes a refrigerant heat exchangingsection that causes a refrigerant flowing from the condenser toward theevaporator and a refrigerant flowing from the evaporator toward thecompressor to exchange heat with each other.
 25. A refrigeration cycleapparatus comprising: a refrigerant circuit including a compressor, acondenser, a decompressing section, and an evaporator; and a refrigerantenclosed in the refrigerant circuit, wherein the refrigerant comprisestrans-1,2-difluoroethylene (HFO-1132(E)), difluoromethane (R32), and2,3,3,3-tetrafluoro-1-propene (R1234yf), wherein when the mass % ofHFO-1132(E), R32, and R1234yf based on their sum in the refrigerant isrespectively represented by x, y, and z, coordinates (x,y,z) in aternary composition diagram in which the sum of HFO-1132(E), R32, andR1234yf is 100 mass % are within the range of a figure surrounded byline segments PS, ST, and TP that connect the following 3 points: pointP (20.5, 51.7, 27.8), point S (21.9, 39.7, 38.4), and point T (8.6,51.6, 39.8), or on these line segments; the line segment PS isrepresented by coordinates (0.0064y²-0.7103y+40.1, y,−0.0064y²-0.2897y+59.9); the line segment ST is represented bycoordinates (0.0082y²-1.8683y+83.126, y, −0.0082y²+0.8683y+16.874); andthe line segment TP is a straight line.
 26. The refrigeration cycleapparatus according to claim 25, wherein the refrigerant circuit furtherincludes a low-pressure receiver provided midway in a refrigerant flowpath extending from the evaporator toward a suction side of thecompressor.
 27. The refrigeration cycle apparatus according to claim 25,wherein the refrigerant circuit further includes a high-pressurereceiver provided midway in a refrigerant flow path extending from thecondenser toward the evaporator.
 28. The refrigeration cycle apparatusaccording to claim 25, wherein the decompressing section comprises afirst decompressing section and a second decompressing section, therefrigerant circuit further includes the first decompressing section,the second decompressing section, and an intermediate-pressure receiverprovided midway in a refrigerant flow path extending from the condensertoward the evaporator, and the intermediate-pressure receiver isprovided between the first decompressing section and the seconddecompressing section in the refrigerant flow path extending from thecondenser toward the evaporator.
 29. The refrigeration cycle apparatusaccording to claim 25, wherein the decompressing section comprises afirst decompressing section and a second decompressing section, therefrigerant circuit further includes the first decompressing section andthe second decompressing section provided midway in a refrigerant flowpath extending from the condenser toward the evaporator, and therefrigeration cycle apparatus further comprises a control unit thatadjusts both a degree of decompression of a refrigerant passing throughthe first decompressing section and a degree of decompression of arefrigerant passing through the second decompressing section.
 30. Therefrigeration cycle apparatus according to claim 25, wherein therefrigerant circuit further includes a refrigerant heat exchangingsection that causes a refrigerant flowing from the condenser toward theevaporator and a refrigerant flowing from the evaporator toward thecompressor to exchange heat with each other.